EP0759499B2 - Dampfturbinenkraftanlage und Dampfturbine - Google Patents

Dampfturbinenkraftanlage und Dampfturbine Download PDF

Info

Publication number
EP0759499B2
EP0759499B2 EP19950113119 EP95113119A EP0759499B2 EP 0759499 B2 EP0759499 B2 EP 0759499B2 EP 19950113119 EP19950113119 EP 19950113119 EP 95113119 A EP95113119 A EP 95113119A EP 0759499 B2 EP0759499 B2 EP 0759499B2
Authority
EP
European Patent Office
Prior art keywords
moving blades
steam
rotor shaft
blades
stage
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.)
Expired - Lifetime
Application number
EP19950113119
Other languages
English (en)
French (fr)
Other versions
EP0759499B1 (de
EP0759499A1 (de
Inventor
Masao Shiga
Ryo Hiraga
Takeshi Onoda
Nobuo Shimizu
Norio Yamada
Mitsuo Kuriyama
Kishio Hidaka
Shigeyoshi Nakamura
Yutaka Fukui
Toshio Fujita
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.)
Hitachi Ltd
Original Assignee
Hitachi Ltd
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
Family has litigation
First worldwide family litigation filed litigation Critical https://patents.darts-ip.com/?family=8219542&utm_source=google_patent&utm_medium=platform_link&utm_campaign=public_patent_search&patent=EP0759499(B2) "Global patent litigation dataset” by Darts-ip is licensed under a Creative Commons Attribution 4.0 International License.
Application filed by Hitachi Ltd filed Critical Hitachi Ltd
Priority to EP19950113119 priority Critical patent/EP0759499B2/de
Priority to DE69525621T priority patent/DE69525621T3/de
Publication of EP0759499A1 publication Critical patent/EP0759499A1/de
Publication of EP0759499B1 publication Critical patent/EP0759499B1/de
Application granted granted Critical
Publication of EP0759499B2 publication Critical patent/EP0759499B2/de
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

Images

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
    • F01D5/12—Blades
    • F01D5/28—Selecting particular materials; Particular measures relating thereto; Measures against erosion or corrosion

Definitions

  • the present invention relates to a novel steam turbine of high efficiency and high temperature, and more particularly to a steam turbine in which a main steam temperature and/or a reheat steam temperature are/is 620 (°C) or above. It also relates to a steam-turbine power plant which employs such steam turbines.
  • austenitic alloys disclosed in the official gazette of Japanese Patent Applications Laid-open No. 180044/1987 and No. 23749/1986, and martensitic steel disclosed in the official gazette of Japanese Patent Applications, Laid-open No. 147948/1992, No. 290950/1990 and No. 371551/1992 are especially known as materials whose high-temperature strengths are superior.
  • An object of the present invention is to provide a steam turbine which permits a heightened steam temperature of 610 - 660 (°C) by heat-resisting ferritic steel and which exhibits a high thermal efficiency, and a steam-turbine power plant which employs the steam turbine.
  • Another object of the present invention is to provide steam turbines whose running temperatures are 610 - 660 (°C) and whose basic designs are substantially the same, and a steam-turbine power plant which employs the steam turbines.
  • the above objects are solved by a steam turbine according to claim 1, a steam turbine power plant according to claim 16 and a coal-fired steam turbine power plant according to claim 18.
  • the dependent claims relate to preferred embodiments of the invention.
  • An embodiment of the present invention consists in a steam-turbine power plant having a high-pressure turbine and an intermediate-pressure turbine which are joined to each other, and low-pressure turbines which are connected in tandem.
  • the improvement comprises that steam inlet of each of the high-pressure and intermediate-pressure turbines which leads to moving blades of a first-stage included in each of the high-pressure and intermediate-pressure turbines being at a temperature of 610 - 660 (°C) (preferably 615 - 640 (°C), and more preferably 620 - 630 (°C)).
  • steam Inlet of each of the low-pressure turbines which leads to moving blades of a first stage included in each of the low-pressure turbines is at a temperature of 380 - 475 (°C) (preferably 400 - 430 (°C)), and a rotor shaft, at least first stage ones of each of the moving blades and the fixed blades, and a casing, which are included in each of the high-pressure and intermediate-pressure turbines and which are exposed to the temperature of the steam Inlet of each of the high-pressure and intermediate-pressure turbines, are made of high-strength martensitic steel which contains 8-13 (weight-%) of Cr.
  • an embodiment of the present invention consists in a steam turbine comprising a rotor shaft, moving blades which are assembled on the rotor shaft, fixed blades which guide Inflow of steam to the moving blades, and an inner casing which holds the fixed blades.
  • the steam flows Into a first stage of the moving blades at a temperature of 610 - 660 (°C) and under a pressure of at least 250 (kg/cm 2 ) (preferably 246-316 (kg/cm 2 )) or 170 - 200 (kg/cm 2 ).
  • the rotor shaft and, at least, first-stage ones of the moving blades and the fixed blades are made of high-strength martensitic steel of fully-tempered martensitic structure which exhibits a 10 5 -hour creep rupture strength of at least 15 (kg/mm 2 ) (preferably 17 (kg/mm 2 )) at a temperature corresponding to the respective steam temperatures (preferably 610 (°C), 625 (°C), 640 (°C), 650 (°C) and 660 (°C)), and which contains 8 - 13 (weight-%), preferably 9.5 - 13 (weight-%) (more preferably 10.5 - 11.5 (weight%)) of Cr, and the inner casing is made of martensitic cast steel which exhibits a 10 5 -hour creep rupture strength of at least 10 (kg/mm 2 ) (preferably 10.5 (kg/mm 2 )) at the temperature corresponding to the respective steam temperatures, and which contains 8 - 13, preferably 8-12, and more preferably 8 - 9.5 (weight
  • an embodiment of the present invention consists in a steam turbine having a rotor shaft, moving blades which are assembled on the rotor shaft, fixed blades which guide inflow of steam to the moving blades, and an inner casing which holds the fixed blades.
  • the rotor shaft and, at least, first-stage ones of the moving blades and the fixed blades are made of high-strength martensitic steel which contains 0.05 - 0.20 (%) of C, at most 0.15 (%) of Si, 0.03 - 1.5 (%) of Mn, 9.5 13 (%) of Cr, 0.05 - 1.0 (%) of Ni, 0.05 - 0.35 (%) of V, 0.01 - 0.20 (%) of Nb, 0.01 - 0.06 (%) of N, 0.05 - 0.5 (%) of Mo, 1.0 - 4.0 (%) of W, 2 - 10 (%) of Co and 0.0005 - 0.03 (%) of B, and which has at least 78 (%) of Fe, the percentages being given in terms of
  • the moving blades at least first stage one thereof, may be made of Ni-based alloy which contains 0.03 - 0.20(%) of C, at most 0.3 (%) of Si, at most 0.2 (%) of Mn, 12 - 20 (%) of Cr, 9 - 20 (%) of Mo, 0.5 - 1.5 (%) of Al, 2 - 3 (%) of Ti, at most 5 (%) of Fe, 0.003 - 0.015 (%) of B.
  • an embodiment of the present invention consists in high-pressure steam turbine having a rotor shaft, moving blades which are assembled on the rotor shaft, fixed blades which guide inflow of steam to the moving blades, and an inner casing which holds the fixed blades, wherein the moving blades are arranged including at least 7 stages on each side in a lengthwise direction of the rotor shaft, except a first stage which is of double flow, and the rotor shaft has a distance (L) of at least 5000 (mm) (preferably 5200 - 5500 (mm)) between centers of bearings in which it is journaled, and a minimum diameter (D) of at least 600 (mm) (preferably 620 - 700 (mm)) at its parts which correspond to the fixed blades, a ratio (L/D) between the distance (L) and the diameter (D) being 8.0 - 9.0 (preferably 8.3 - 8.7), and it is made of high-strength martensitic steel which contains 9 - 13 (weight-%) of Cr.
  • an embodiment of the present invention consists in the an intermediate-pressure steam turbine having a rotor shaft, moving blades which are assembled on the rotor shaft, fixed blades which guide inflow of steam to the moving blades, and an inner casing which holds the fixed blades, wherein the moving blades have a double-flow construction in which at least 6 stages are included on each side in a lengthwise direction of the rotorshaft,
  • the rotor shaft has a distance (L) of at least 5000 (mm), preferably 5200 (mm) (more preferably 5300 - 5800 (mm)) between centers of bearings in which it is journaled, and a minimum diameter (D) of at least 600 (mm), preferably 620 (mm) (more preferably 620 - 680 (mm)) at its parts which correspond to the fixed blades, a ratio (UD) between the distance
  • an embodiment of the present invention consists in a low-pressure steam turbine having a rotor shaft, moving blades which are assembled on the rotor shaft, fixed blades which guide inflow of steam to the moving blades, and an inner casing which holds the fixed blades, wherein the moving blades have a double-flow construction in which at least 8 stages are included on each side in a lengthwise direction of the rotor shaft, in a bilaterally symmetric arrangement on both sides, and in which the first stages of the arrangement are assembled on a central part of the rotor shaft in the lengthwise direction, the rotor shaft has a distance (L) of at least 7200 (mm) (preferably 7400 - 7600 (mm)) between centers of bearings In which it is journaled, and a minimum diameter (D) of at least 1150 (mm) (preferably 1200 - 1350 (mm)) at its parts which correspond to the fixed blades, a ratio (L/D) between the distance (L) and the diameter (D) being 5.4 - 6.3 (L
  • an embodiment of the present invention consists in a steam-turbine power plant having a high-pressure turbine and an intermediate-pressure turbine which are joined to each other, and two low-pressure turbines which are connected in tandem, wherein that steam inlet of each of the high-pressure and intermediate-pressure turbines which leads to moving blades of a first stage included in each of the high-pressure and intermediate-pressure turbines is at a temperature of 610 - 660 (°C), that steam inlet of the low-pressure turbine which leads to moving blades of a first stage included in the low-pressure turbine is at a temperature of 380 - 475 (°C), the first-stage moving blade of the high-pressure turbine, and that part of a rotor shaft of the high-pressure turbine on which the first-stage moving blade is assembled are held at metal temperatures which are not, at least, 40 (°C) lowerthan the temperature of the steam inlet of the high-pressure turbine leading to the first-stage moving blade (preferably, the metal temperatures are 20 - 35 (°C) lower than the steam temperature
  • an embodiment of the present invention consists in a coal-fired power plant having a coal-fired boiler, steam turbines which are driven by steam developed by the boiler, and one or more, preferably two, generators which are driven by the steam turbines and which can generate an output of at least 1000 (MW), wherein the steam turbines include a high-pressure turbine, an intermediate-pressure turbine which is joined to the high-pressure turbine, and two low-pressure turbines, that steam inlet of each of the high-pressure and intermediate-pressure turbines which leads to moving blades of a first stage included in each of the high-pressure and intermediate-pressure turbines is at a temperature of 610 - 660 (°C), that steam inlet of the low-pressure turbine which leads to moving blades of af first stage included in the low-pressure turbine is at a temperature of 380 - 475 (°C), the steam heated by a superheater of the boiler to a temperature which is at least 3 (°C) (preferably 3 -10 (°C), more preferably 3 - 7
  • an embodiment of the present invention consists in the low-pressure steam turbine stated before; wherein that steam inlet of the low-pressure turbine which leads to a first-stage one of the moving blades is at a temperature of 380 - 475 (°C) (preferably 400 - 450 (°C)), and the rotor shaft is made of low-alloy steel which contains 0.2 - 0.3 (%) of C, at most 0.05 (%) of Si, at most 0.1 (%) of Mn, 3.25 - 4.25 (%) of Ni, 1.25 - 2.25 (%) of Cr, 0.07 - 0.20 (%) of Mo, 0.07 - 0.2 (%) of V and at least 92.5 (%) of Fe, the percentages being given in terms of weight.
  • an embodiment of the present invention consists in the high-pressure steam turbine stated before; wherein the moving blades are arranged including at least 7 stages (preferably 9-12 stages), and they have lengths of 35 - 210 (mm) in a region from an upstream side of the steam flow to a downstream side thereof, diameters of those parts of the rotor shaft on which the moving blades are assembled are larger than diameters of those parts of the rotor shaft which correspond to the fixed blades; and widths of the moving-blade assembling parts of the rotor shaft in an axial direction of the rotor shaft being stepwise larger on the downstream side than on the upstream side at, at least, 3 stages (preferably 4 - 7 stages), and the ratios of these widths to the lengths of the moving blades decrease from the upstream side toward the downstream side within a range of 0.6 - 1.0 (preferably 0.65 - 0.95).
  • an embodiment of the present invention consists in the improvement wherein the moving blades are arranged in at least 7 stages, and they have lengths of 35 - 210 (mm) In a region from an upstream side of the steam flow to a downstream side thereof, ratios between the lengths of the moving blades of the respectively adjacent stages are at most 1.2 (preferably 1.10-1.15), and they increase gradually toward the downstream side, and the lengths of the moving blades are larger on the downstream side than on the upstream side.
  • an embodiment of the present invention consists in the improvement wherein the moving blades are arranged in at least 7 stages, and they have lengths of 35 - 210 (mm) in a region from an upstream side of the steam flow to a downstream side thereof, and widths of those parts of the rotor shaft which correspond to the fixed blades, the widths being taken in an axial direction of the rotor shaft, are stepwise smaller on the downstream side than on the upstream side at, at least, 2 stages (preferably 2-4 stages), and the ratios of these widths to the lengths of the downstream-side moving blades decrease stepwise toward the downstream side within a range of 0.65 - 1.8 (preferably 0.7 - 1.7).
  • an embodiment of the present invention consists in the intermediate-pressure steam turbine stated before, wherein the moving blades have a double-flow construction in which at least 6 stages (preferably 6 - 9 stages) are included on each side in a lengthwise direction of the rotorshaft, in a bilaterally symmetric arrangement on both sides, and they have lengths of 100 - 300 (mm) in a region from an upstream side of the steam flow to a downstream side thereof, diameters of those parts of the rotor shaft on which the moving blades being assembled are larger than diameters of those parts of the rotor shaft which correspond to the fixed blades, and widths of the moving-blade assembling parts of the rotor shaft in an axial direction of the rotor shaft being stepwise larger on the downstream side than on the upstream side at, at least, 2 stages (preferably 3 - 6 stages), and the ratios of these widths to the lengths of the moving blades decrease from the upstream side toward the downstream side within a range of 0.45 - 0.75 (preferably 0.5 - -
  • an embodiment of the present invention consists in the improvement wherein the moving blades have a double-flow construction in which at least 6 stages are included on each side in a lengthwise direction of the rotor shaft, in a bilaterally symmetric arrangement on both sides, and they have lengths of 100 - 300 (mm) in a region from an upstream side of the steam flow to a downstream side thereof, and the lengths of the respectively adjacent moving blades are larger on the downstream side than on the upstream side, and their ratios are at most 1.3 (preferably 1.1 -1.2) and increase gradually toward the downstream side.
  • an embodiment of the present invention consists in the improvement wherein the moving blades have a double-flow construction in which at least 6 stages are included on each side in a lengthwise direction of the rotor shaft, in a bilaterally symmetric arrangement on both the sides, and they have lengths of 100 - 300 (mm) in a region from an upstream side of the steam flow to a downstream side thereof, and widths of those parts of the rotor shaft which correspond to the fixed blades, the widths being taken in an axial direction of the rotor shaft, are stepwise smaller on the downstream side than on the upstream side at, at least, 2 stages (preferably 3 - 6 stages), and the ratios of these widths to the lengths of the downstream-side moving blades decrease stepwise toward the downstream side within a range of 0.45 -1.60 (preferabl 0.5-1.5).
  • an embodiment of the present invention consists in the low-pressure steam turbine stated before; wherein the moving blades have a double-flow construction in which at least 8 stages (preferably 8 - 10 stages) are included on each side in a lengthwise direction of the rotor shaft, in a bilaterally symmetric arrangement on both sides, and they have lengths of 90 - 1300 (mm) in a region from an upstream side of the steam flow to a downstream side thereof; diameters of those parts of the rotor shaft on which the moving blades are assembled are larger than diameters of those parts of the rotor shaft which correspond to the fixed blades; and widths of the moving-blade assembling parts of the rotor shaft in an axial direction of the rotor shaft are stepwise larger on the downstream side than on the upstream side at, at least, 3 stages (preferably 4 - 7 stages), and the ratios of these widths to the lengths of the moving blades decrease from the upstream side toward the downstream side within a range of 0.15 -1.0 (preferably 0.15 - 0.9
  • an embodiment of the present invention consists in the improvement wherein the moving blades have a double-flow construction in which at least 8 stages are included on each side in a lengthwise direction of the rotor shaft, in a bilaterally symmetric arrangement on both sides, and they have lengths of 90 - 1300 (mm) in a region from an upstream side of the steam flow to a downstream side thereof; and the lengths of the moving blades of the respectively adjacent stages are larger on the downstream side than on the upstream side, and their ratios increase gradually toward the downstream side within a range of 1.2 - 1.7 (preferably 1.3 - 1.6).
  • an embodiment of the present invention consists in the improvement wherein the moving blades have a double-flow construction in which at least 8 stages are included on each side in a lengthwise direction of the rotor shaft, in a bilaterally symmetric arrangement on both sides, and they have lengths of 90 - 1300 (mm) in a region from an upstream side of the steam flow to a downstream side thereof; and widths of those parts of the rotor shaft which correspond to the fixed blades, the widths being taken in an axial direction of the rotor shaft, are stepwise larger on the downstream side than on the upstream side at, at least, 3 stages (preferably 4 - 7 stages), and the ratios of these widths to the lengths of the respectively adjacent moving blades on the downstream side decrease stepwise toward the downstream side within a range of 0.2- 1.4 (preferably 0.25 - 1.25).
  • an embodiment of the present invention consists in a high-pressure steam turbine having a rotor shaft, moving blades which are assembled on the rotor shaft, fixed blades which guide inflow of steam to the moving blades, and an inner casing which holds the fixed blades; wherein the moving blades are arranged including at least 7 stages; diameters of those parts of the rotor shaft which correspond to the fixed blades are smaller than diameters of those parts of the rotor shaft which correspond to the assembled moving blades; widths of the rotor shaft parts corresponding to the fixed blades, in an axial direction of the rotor shaft are stepwise larger on an upstream side of the steam flow than on a downstream side thereof at, at least, 2 of the stages (preferably 2-4 stages), and the width between the final stage of the moving blades and the stage thereof directly preceding the final stage is 0.75 - 0.95 (preferably 0.8 - 0.9, more preferably 0.84 - 0.88) times as large as the width between the second stage and the third stage of the moving blades; and width
  • an embodiment of the present invention consists in an intermediate-pressure steam turbine having a rotor shaft, moving blades which are assembled on the rotor shaft, fixed blades which guide inflow of steam to the moving blades, and an inner casing which holds the fixed blades; wherein the moving blades are arranged including at least 6 stages; diameters of those parts of the rotor shaft which correspond to the fixed blades are smaller than diameters of those parts of the rotor shaft which correspond to the assembled moving blades; widths of the rotor shaft parts corresponding to the fixed blades, in an axial direction of the rotor shaft are stepwise larger on an upstream side of the steam flow than on a downstream side thereof at, at least, 2 of the stages (preferably 3 - 6 stages), and the width between the final stage of the moving blades and the stage thereof directly preceding the final stage is 0.55 - 0.8 (preferably 0.6 - 0.7) times as large as the width between the first stage and the second stage of the moving blades; and widths of the rotor shaft parts
  • an embodiment of the present invention consists in a low-pressure steam turbine having a rotor shaft, moving blades which are assembled on the rotor shaft, fixed blades which guide inflow of steam to the moving blades, and an inner casing which holds the fixed blades; wherein the moving blades have a double-flow construction in which at least 8 stages are included on each side in an axial direction of the rotor shaft, in a bilaterally symmetric arrangement on both sides; diameters of those parts of the rotor shaft which correspond to the fixed blades are smaller than diameters of those parts of the rotor shaft which correspond to the assembled moving blades; widths of the rotor shaft parts corresponding to the fixed blades, in the axial direction of the rotor shaft are stepwise larger on an upstream side of the steam flow than on a downstream side thereof at, at least, 3 of the stages (preferably 4-7 stages), and the width between the final stage of the moving blades and the stage thereof directly preceding the final stage is 1.5 - 2.5 (preferably 1.7 - 2.2) times
  • alloy contents should preferably be controlled so as to become 4 - 8 in terms of a Cr equivalent which is computed by a formula given below, in order that a superior high-temperature strength, a low-temperature toughness and a high fatigue strength may be attained from the fully-tempered martensitic structure.
  • alloy contents should preferably be controlled so as to become 4 - 10 in terms of the Cr equivalent which is computed by the formula given below, in order that a superior high-temperature strength, a low-temperature toughness and a high fatigue strength may be attained by controlling the alloying constituents so as to establish a martensitic structure tempered to at least 95 (%), In other words, containing at most 5 (%) of ⁇ (delta) ferrite.
  • Cr equivalent Cr + 6Si + 4Mo + 1.5W + 11V + 5Nb - 40C - 30N - 30B - 2Mn - 4Ni - 2Co
  • the 12Cr heat-resisting steel in an embodiment of the present invention especially in a case where the steel is used with steam at or above 621 (°C), it should preferably be endowed with a 625-°C 10 5 -h creep rupture strength of at least 10 (kgf/mm 2 ) and a room-temperature absorbed impact energy of at least 1 (kgf-m).
  • the constituent C is an element which is indispensable to ensuring hardenability upon quenching, and precipitating carbides in a tempering heat-treatment process so as to enhance a high-temperature strength.
  • the element C is required at a level of at least 0.05 (%) in order to attain a high tensile strength.
  • the C content is restricted to within 0.05 - 0.20 (%). It should desirably be within 0.08 - 0.14 (%), and particularly preferably be within 0.09 - 0.14 (%).
  • the constituent Mn (manganese) is added as a deoxidizer etc., and the deoxidizing effect thereof is achieved by a small amount of addition.
  • a large amount of addition exceeding 1.5 (%) is unfavorable because it lowers the creep rupture strength.
  • a range of 0.03 - 0.20 (%) or a range of 0.3 - 0.7 (%) is preferable, and a range of 0.35 - 0.65 (%) is more preferable for the latter.
  • the Mn content is made lower, a higher strength is attained.
  • the workability of the ferritic steel improves.
  • the constituent Si (silicon) is also added as a deoxidizer, but the Si deoxidation is dispensed if a steelmaking technique such as the vacuum C deoxidation or the like is made.
  • a lower Si content is effective to prevent the production of the deleterious ⁇ ferrite structure, and to prevent the degradation of the toughness of the ferritic steel attributed to grain-boundary segregation, etc. Accordingly, the addition of the constituent Si needs to be suppressed to 0.15 (%) or below.
  • the Si content of the ferritic steel should desirably be at most 0.07 (%), and should particularly preferably be at most 0.05 (%).
  • the constituent Ni is an element which is very effective to heighten the toughness and to prevent the production of the ⁇ ferrite.
  • the addition of the element Ni at a level of less than 0.05 (%) is unfavorable because it has an insufficient effect, and the addition thereof at more than 1.0 (%) is also unfavorable because of degradation in the creep rupture strength.
  • a range of 0.3 - 0.7 (%) is preferable, and a range of 0.4 - 0.65 (%) is more preferable.
  • the constituent Cr is an element which is indispensable to enhancing the high-temperature strength and high-temperature oxidation resistance of the ferritic steel.
  • the element Cr is required at least 9 (%).
  • the Cr content exceeds 13 (%), the deleterious ⁇ ferrite structure is produced, which lowers the high-temperature strength and the toughness. Therefore, the Cr content is restricted to within 9-12 (%).
  • a range of 10 -12 (%) is preferable, and a range of 10.8 - 11.8 (%) is more preferable.
  • the addition of the constituent Mo is intended to enhance the high-temperature strength.
  • Mo molybdenum
  • W tungsten
  • Mo addition at a level of exceeding 0.5 (%) lowers the toughness and fatigue strength of the ferritic steel. Therefore, the Mo content is limited to, at most, 0.5 (%).
  • a range of 0.05 - 0.45 (%) is preferable, and a range of 0.1 - 0.3 (%) is more preferable.
  • the constituent W suppresses the coarsening of carbides due to the agglomerations thereof at high temperatures, and it turns the matrix of the ferritic steel into a solid solution and strengthens this matrix. It is therefore effective to remarkably enhance the long-term strength of the ferritic steel at the high temperatures of at least 620 (°C).
  • the W content of the ferritic steel should preferably be 1- 1.5 (%) at 620 (°C), 1.6 - 2.0 (%) at 630 (°C), 2.1 - 2.5 (%) at 640 (°C), 2.5 - 3.0 (%) at 650 (°C) and 3.1 - 3.5 (%) at 660 (°C).
  • the W content exceeds 3.5 (%), the ⁇ ferrite is produced, which lowers the toughness. Therefore, the W content is restricted to within 1 - 3.5 (%). Especially, a range of 2.4 - 3.0 (%) is preferable, and a range of 2.5 - 2.8 (%) is more preferable.
  • the constituent V (vanadium) is effective to heighten the creep rupture strength by precipitating the carbonitrides of this constituent V.
  • V content of the ferritic steel is less than 0.05 (%), the effect is insufficient.
  • V content exceeds 0.3 (%) the 8 ferrite is produced, which lowers the fatigue strength.
  • a range of 0.10 - 0.25 (%) is preferable, and a range of 0.15 - 0.25 (%) is more preferable.
  • the constituent Nb is an element which is very effective to precipitate NbC (niobium carbide) and enhance the high-temperature strength.
  • NbC niobium carbide
  • the constituent Nb is an element which is very effective to precipitate NbC (niobium carbide) and enhance the high-temperature strength.
  • the element Nb is added in an excessively large amount, the coarse grains of eutectic NbC appear, especially in a large-sized steel ingot, which causes significant lowering of the strength and precipitation of the ⁇ ferrite, which lowers the fatigue strength. It is therefore necessary to suppress the amount of the element Nb to 0.20 (%) or below.
  • the Nb amount is less than 0.01 (%), the effect is insufficient.
  • a range of 0.02 - 0.15 (%) is preferable, and a range of 0.04 - 0.10 (%) is more preferable.
  • the constituent Co is an important element, and is a feature which distinguishes the present invention from the prior-art techniques.
  • the high-temperature strength is remarkably improved, and the toughness is also heightened.
  • These effects are considered to be based on the interaction between the elements Co and W, and they are the characterizing phenomena of the alloy of the present invention containing the element W in the amount of at least 1 (%).
  • the lower limit of the Co amount in the alloy of the present invention is set at 2.0 (%).
  • the element Co is added in excess, greater effects are not attained, and moreover, the ductility of the ferritic steel is lowered.
  • the upper limit of the Co amount is set at 10 (%).
  • the Co amount should desirably be selected from 2 - 3 (%) for 620 (°C), 3.5 - 4.5 (%) for 630 (°C), 5 - 6 (%) for 640 (°C), 6.5 - 7.5 (%) for 650 (°C), and 8 - 9 (%) for 660 (°C). But an efficient strength can be obtained by addition of at least 2 (%) of Co for any degree of temperature at most 650 (°C).
  • the constituent N is also an important element and is a feature which distinguishes the present invention from the prior-art techniques.
  • the element N is effective to improve the creep rupture strength and to prevent the production of the 8 ferrite structure.
  • the N content of the ferritic steel is less than 0.01 (%), the effects are not sufficient.
  • the N content exceeds 0.05 (%), the toughness is lowered, and the creep rupture strength is also lowered.
  • a range of 0.01 - 0.03 (%) is preferable, and a range of 0.01 - 0.025 (%) is more preferable.
  • the constituent B (boron) is effective to enhance the high-temperature strength by the action of intensifying grain boundaries, and the action of turning into solid solutions in carbides M 23 C 6 to hinder the M 23 C 6 type carbides from coarsening due to the agglomerations thereof. It is effective to add the constituent B to a level in excess of 0.001 (%). However, when the B content exceeds 0.03 (%), the weldability and forgeability of the ferritic steel are degraded. Therefore, the B content is limited to within 0.001 - 0.03 (%). It should desirably be 0.001 - 0.01 (%) or 0.01 - 0.02 (%).
  • the addition of the constituent/constituents Ta (tantalum), Ti (titanium) or/and Zr (zirconium) is effective to heighten the toughness.
  • a sufficient effect is attained by adding at most 0.15 (%) of Ta, at most 0.1 (%) of Ti or/and at most 0.1 (%) of Zr singly or in combination.
  • the constituent Ta is added at a level of 0.1 (%) or above, the addition of the constituent Nb (niobium) can be omitted.
  • the rotor shaft and, at least, the first-stage ones of the moving blades and fixed blades in the present invention should preferably be made for a steam temperature of 620 - 630 (°C) out of steel of fully-tempered martensitic structure which contains 0.09 - 0.20 (%) of C, at most 0.15 (%) of Si, 0.05 - 1.0 (%) of Mn, 9.5 - 12.5 (%) of Cr, 0.1 - 1.0 (%) of Ni, 0.05 - 0.30 (%) of V, 0.01 - 0.06 (%) of N, 0.05 - 0.5 (%) of Mo, 2 - 3.5 (%) of W, 2 - 4.5 (%) of Co, 0.001 - 0.030 (%) of B, and at least 77 (%) of Fe (iron).
  • a high strength is attained by decreasing the Mn content to 0.03 - 0.2 (%) and the B content to 0.001 - 0.01 (%) for both the aforementioned temperatures.
  • the martensitic steel should particularly preferably contain 0.09 - 0.20 (%) of C, 0.1 - 0.7 (%) of Mn, 0.1 - 1.0 (%) of Ni, 0.10 - 0.30 (%) of V, 0.02 - 0.05 (%) of N, 0.05 - 0.5 (%) of Mo, and 2 - 3.5 (%) of W, along with 2 - 4 (%) of Co and 0.001 - 0.01 (%) of B for a temperature of or below 630 (°C) or 5.5 - 9.0 (%) of Co and 0.01 - 0.03 (%) of B for a temperature of 630 - 660 (°C).
  • the martensitic steel including the former percentage of Co can be used at the temperature between 620 - 650 (%).
  • the Cr equivalent which is obtained by the formula mentioned before is set at 4 - 10.5 for the rotor shafts of the high-pressure and intermediate-pressure steam turbines, and a range of 6.5 - 9.5 is particularly preferable therefor. The same applies to the other components of these steam turbines stated before.
  • the tempered martensitic structure which is homogeneous, is favorable for the heat-resisting ferritic steel.
  • the Cr equivalent which is computed by the formula mentioned before must be set at, at most, 10 by controlling the alloy contents.
  • the Cr equivalent when the Cr equivalent is too small, it lowers the creep rupture strength, and hence, it must be set at, at least, 4.
  • a range of 5 - 8 is preferable as the Cr equivalent.
  • At least one of the rotor shaft, each moving blade and each fixed blade in the present invention should preferably be made of steel which satisfies at least one of conditions; a (B + N) content of 0.050 (%) or below, an (N/B) ratio of 1.5 or above (preferably, 1.5 - 2.0), a (B/Co) ratio of 0.0035 or above (preferably, 0.0035 - 0.008, and more preferably, 0.004 - 0.006), a (Co/Mo) ratio of 18 or below (preferably, 8-18, and more preferably, 11 - 16), and a (Co/Nb) ratio of 30 or above (preferably, 30 - 70).
  • Steel which satisfies all the conditions, is more preferable. These elements correlate organically.
  • the element C When added at least 0.03 (%), the element C (carbon) precipitates carbides during use in a solid-solution state or at high temperatures, to thereby enhance the yield strength and creep strength of the alloy at high temperatures.
  • the C content should preferably be 0.03 - 0.15 (%).
  • the element Cr (chromium) needs to be contained at least 12 (%) in order to enhance the yield strength and creep strength of the alloy at high temperatures and to further enhance the high-temperature oxidation resistance and sulfurization-corrosion resistance of the alloy, in the solid-solution state of this element Cr in the alloy.
  • the Cr content exceeds 20 (%), the ⁇ phase of steel is precipitated to lower the contraction percentage of the alloy in the high-temperature tensile test thereof. Therefore, the preferable range of the Cr content is 12 - 20 (%).
  • the element Mo mobdenum
  • the element Mo When added in excess of 9 (%), the element Mo (molybdenum) remarkably enhances the yield strength of the alloy at high temperatures and also the creep rupture strength thereof, in the solid-solution state of this element Mo in the alloy.
  • the element Mo when contained in excess of 20 (%), the element Mo abruptly degrades the yield strength at the high temperatures contrariwise. Further, it spoils the cold working property of the alloy, and it precipitates the ⁇ phase to lower the contraction percentage of the alloy in the high-temperature tension thereof. Therefore, the preferable range of the Mo content is 12 - 20 (%).
  • the element Co When added at most 12 (%), the element Co (cobalt) remarkably enhances the creep rupture strengths of the alloy at the room temperature and at high temperatures, in the solid-solution state of this element Co in the alloy. However, when contained in excess of 12 (%), the element Co abruptly degrades the high-temperature ductility of the alloy, and it precipitates the ⁇ phase to lower the contraction percentage of the alloy in the high-temperature tension thereof. Therefore, the preferable range of the Co content is 5 - 12 (%).
  • the element Al (aluminum) turns into a solid solution in the alloy and precipitates the ⁇ prime phase of steel during use at high temperatures for a long time period, to thereby enhance the yield strength and creep rupture strength of the alloy in the high-temperature tension thereof.
  • the preferable range of the Al content is 0.5 - 1.2 (%).
  • the element TI titanium
  • the element TI titanium
  • the contraction percentage of the alloy degrades in the high-temperature tension thereof.
  • the element Fe (iron) lowers the creep rupture strength of the alloy, the containment thereof ought to be avoided as far as possible. Even in a case where the element Fe is contained as an impurity, it ought to be limited to, at most, 5 (%).
  • the elements Si (silicon) and Mn (manganese) are respectively added at most 0.3 (%) and at most 0.2 (%) as deoxidizers or in order to enhance the hot working property of the alloy. It is the most preferable, however, to add neither of these elements Si and Mn.
  • the element B (boron) segregates at the austenitic grain boundary of steel in a very small amount, and enhances the creep rupture strength and high-temperature ductility of the alloy.
  • This element B is effective when contained at least 0.003 (%). However, it degrades both the hot plastic working property and high-temperature ductility of the alloy when contained in excess of 0.015 (%). Therefore, the B content ought to be set at 0.003 - 0.015 (%).
  • the element Zr (zirconium) is an intense element for forming a carbide. When added in a very small amount, this element Zr enhances the creep rupture strength of the alloy owing to its action synergic with the formation of other carbides by the elements Ti etc. However, when these elements are added in excess, the ductility of the alloy at high temperatures degrades for such reasonsthatthe binding powers of grain boundaries lower and that coarse carbide grains are formed.
  • the element Mg at most 0.1 (%), the rare-earth elements at most 0.5 (%) and the element Zr at most 0.5 (%) it is particularly preferable to add the element Mg 0.005 - 0.05 (%), the rare-earth elements 0.005 - 0.1 (%) and the element Zr 0.01 - 0.2 (%).
  • the alloy in an embodiment of the present invention is subjected to a treatment for turning an ingot into a solid solution, and thereafter to a treatment for ageing.
  • the solid-solution treatment is carried out by holding the ingot at 1,050- 1,200 (°C) for 30 (minutes) - 10 (hours), and subsequently cooling the heated ingot with water, air or the like.
  • the water cooling is performed by throwing the alloy at a predetermined temperature into the body of water. Alternatively, when the alloy is flat, water is sprayed onto the surfaces of the alloy at a predetermined temperature.
  • the ageing treatment is carried out in such a way that the material subjected to the above solid-solution treatment is heated and held at 700 - 870 (°C) for 4 - 24 (hours).
  • the alloy in an embodiment of the present invention should preferably be molten In a non-oxidizing atmosphere.
  • Raw materials to be used for the alloy are pure metals. From the standpoints of heightening the available percentages of the alloy elements and preventing the dispersion of the alloy composition, therefore, the raw materials should preferably be heated in vacuum until they are about to melt and drop, and they are thereafter molten by introducing a non-oxidizing gas.
  • the raw materials thus molten are subjected to vacuum arc remelting or electroslag remelting. Then, the desired alloy can be obtained.
  • Each of the Ni-based precipitation-strengthened alloys should exhibit a preferable tensile strength of 90 (kg/mm 2 ) or above, or a more preferable one of 100 (kg/mm 2 ) or above, at the room temperature, and a preferable tensile strength of 80 (kg/mm 2 ) or above, at 732 (°C). It should also exhibit a preferable elongation percentage of 10 (%) or above.
  • alloying raw materials to be brought into the desired composition are melted in an electric furnace, the molten materials are deoxidized by carbon vacuum deoxidation, the deoxidized materials are cast into a metal mold, and the molded article is forged into an electrode.
  • the electrode thus fabricated is subjected to electroslag remelting, and the resulting slag is forged and formed into the shape of the rotor.
  • the forging must be carried out at a temperature of 1150 (°C) or below in order to prevent forging cracks.
  • the forged steel After the forged steel has been annealed, it is heated to 1000 - 1100 (°C) and then quenched, and it is tempered twice in the sequence of a temperature range of 550 - 650 (°C) and a temperature range of 670 - 770 (°C).
  • the steam turbine rotor which is usable in steam at or above 620 (°C) can be manufactured.
  • an ingot is prepared in such a way that the alloying raw materials to be brought into the desired composition are melted by vacuum melting, and that the molten materials are cast in a metal mold in vacuum.
  • the ingot is hot-forged into a predetermined shape at the same temperature as stated before. After the forged ingot has been heated to 1050 - 1150 (°C), it is subjected to water cooling or oil quenching.
  • the resulting ingot is tempered in a temperature range of 700 - 800 (°C), and it is machined into the component of desired shape.
  • the vacuum melting is carried out under a vacuum condition of 1,33 ⁇ 10 -2 to 13,3 Pa (10 -1 - 10 -4 (mmHg)).
  • the heat-resisting steel can be applied to all the stages of the blades and nozzles of the high-pressure portion and intermediate-pressure portion, they are especially necessary for the first stages of both the sorts of component.
  • the steam-turbine rotor shaft made of the 12 weight-% Crtype martensitic steel should preferably be so constructed that buildup welding layers of good bearing characteristics are formed on the surface of the parent metal forming each journal portion of the rotor shaft. More specifically, the buildup welding layers are formed in the number of, at least 3, preferably 5 -10 by the use of a weld metal being steel.
  • the Cr content of the steel as the weld metal is lowered successively from the first layer to any of the second -fourth layers, whereas the layers of and behind the fourth layer are formed of the steel having an identical Cr content.
  • the Cr content of the weld metal for the deposition of the first layer is rendered about 2 - 6 (weight-%) less than that of the parent metal, and the Cr contents of the welding layers of and behind the fourth layer are set at 0.5 - 3 (weight-%), preferably at 1 - 2.5 (weight%).
  • the buildup welding is favorable for the improvement of the bearing characteristics of the journal portion In view of the highest safety, but it becomes very difficuft due to increase in the B content of the steel. Therefore, in the case where the B content is set at 0.02 (%) or above in order to attain a higher strength, it is recommended to adopt a construction in which the journal portion is inserted into a sleeve made of low-alloy steel having a Cr content of 1-3 (%), through shrinkage fit.
  • the material composition of the sleeve is the same as that of the buildup welding layers to be explained later.
  • the buildup welding layers are preferably in the number of 5 - 10. Abrupt decrease In the amount of Cr in the first welding layer causes the development of high residual tensile stress or welding cracks, so that the Cr content of the weld metal of the first welding layer cannot be sharply lowered. As stated before, therefore, the Cr contents need to be gradually lowered with the enlarged number of welding layers. Further, since the desired Cr content and a desired thickness need to be held as the surface layer of the journal portion, the welding layers need to be in the number of 5 or more. By the way, even when the number of welding layers is larger than 10, no greater effect is achieved.
  • the buildup welding layers must not have their composition influenced by the parent metal and need to be endowed with the desired composition as well as the desired thickness.
  • three layers are required as a thickness for preventing the influence of the parent metal.
  • layers of desired characteristics need to be stacked on the three layers to a desired thickness, and at least two layers are required as the desired thickness.
  • a thickness of about 18 (mm) is required as the desired thickness of the finally finished buildup welding layers.
  • at least five buildup welding layers are necessitated even when a final finish margin to be machined is excluded.
  • the third layer et seq.
  • the composition of the fourth welding layer et seq. should preferably contain in terms of weight, 0.01 - 0.1 (%) of C,0.3 - 1 (%) of Si, 0.3 - 1.5 (%) of Mn, 0.5 - 3 (%) of Cr and 0.1 -1.5 (%) of Mo, the balance being Fe.
  • the Cr content is lowered successively from the first layer to any of the second - fourth layers.
  • welding rods whose Cr contents are gradually lowered are used for the respective layers.
  • the buildup welding layers of the desired composition can be formed without incurring the problem of lowered ductility or welding cracks of the first-layerwelding zone attributed to the sharp decrease of the chromium content in the first-layer welding zone. In this way, it is possible to form buildup welding layers in which the chromium contents in the vicinities of the parent metal and the first-layer zone do not exhibit a very large difference, and in which the final layer has the good bearing characteristics as stated above.
  • the weld metal which is applied to the first-layer welding has its chromium content rendered about 2 - 6 (weight-%) lower than the chromium content of the parent metal.
  • the Cr content of the weld metal is less than 2 (%) that of the parent metal, the pertinent Cr content of the buildup welding layer cannot be lowered sufficiently, and the effect is slight.
  • the value exceeds 6 (%) the Cr content of the buildup welding layer lowers suddenly from that of the parent metal, and the difference between the Crcontents gives rise to a large difference between the coefficients of thermal expansion of both the metals, to thereby cause development of high residual tensile stress or welding cracks.
  • the buildup welding layer of lower Cr content has larger coefficient of thermal expansion than the parent metal and is formed with the high residual tensile stress by the welding. Therefore, the welding with steel of still lower Cr content produces a hard layer due to the high residual stress and causes development of welding cracks. Accordingly, the Cr content of the weld metal needs to be set at, at most, 6 (%) smaller than that of the parent metal. Owing to the use of such a weld metal, the chromium content of the first-layer welding layer becomes lower than that of the parent metal by as little as about 1 - 3 (%) because the weld metal mixes with the parent metal. Thus, favorable welding is attained.
  • the layers of and behind the fourth layer need to be formed using weld metal which is made of steel having an identical Cr content.
  • the buildup welding layers up to the third layer are influenced by the composition of the parent metal. Since, however, the fourth buildup welding layer et seq. are composed only of the employed weld metal without this influence, they can be formed to satisfy the characteristics required for the journal portion of the steam-turbine rotor shaft. Besides, as stated before, the thickness of the buildup welding layers required for the large-sized structural member operating as the steam-turbine rotor shaft is about 18 (mm).
  • the final layer which satisfies the characteristics required for the journal portion as stated before can be formed having the sufficient thickness.
  • the NI/W ratio is controlled to 0.25 - 0.75, thereby obtaining the casing material of the heat-resisting cast steel which meets a 625-°C 10 5 -h creep rupture strength of at least 9 (kgf/mm 2 ) and a room-temperature absorbed impact energy of at least 1 (kgf-m) that are required of the high-pressure and intermediate-pressure inner casings, main-steam stop valve and control valve casing of the turbine under the ultra-supercritical pressure of at least 250 (kgf/cm 2 ) at 621 (°C).
  • the 12Cr heat-resisting steel in an embodiment of the present invention is used in the steam at or above 621 (°C), it must be endowed with the 625-°C 10 5 -h creep rupture strength of et least 9 (kgf/mm 2 ) and the room-temperature absorbed impact energy of at least 1 (kgf-m). Further, in order to ensure a still higher reliability, this steel should preferably be endowed with a 625-°C 10 5 -h creep rupture strength of at least 10 (kgf/mm 2 ) and a room-temperature absorbed impact energy of at least 2 (kgf-m).
  • the constituent C (carbon) is an element which is required at a level of least 0.06 (%) in order to attain a high tensile strength.
  • the C content exceeds 0.16 (%), the steel comes to have an unstable metallographic structure and degraded the long-time creep rupture strength thereof when exposed to high temperatures for a long time period. Therefore, the C content is restricted to within 0.06 - 0.16 (%). It should preferably be within 0.09 - 0.14 (%).
  • the constituent N is effective to improve the creep rupture strength and to prevent the production of the 8 ferrite structure.
  • the N content of the steel is less than 0.01 (%), the effects are not sufficient.
  • the N content exceeds 0.1 (%), no remarkable effects are attained.
  • the toughness is lowered, and the creep rupture strength is also lowered.
  • a range of 0.02 - 0.4 (%) is preferable.
  • the constituent Mn (manganese) is added for a deoxidizer, and the effect thereof is achieved by a small amount of addition.
  • a large amount of addition exceeding 1 (%) is unfavorable because it lowers the creep rupture strength.
  • a range of 0.4 - 0.7 (%) is preferable.
  • the constituent Si (silicon) is also added as a deoxidizer, but the Si deoxidation is dispensed with when the steelmaking technique employed is vacuum C deoxidation or the like.
  • a lower Si content is effective to prevent the production of the deleterious ⁇ ferrite structure. Accordingly, the addition of the constituent Si needs to be suppressed to 0.5 (%) or below.
  • the Si content of the steel should preferably be 0.1 - 0.4 (%).
  • the constituent V (vanadium) is effective to heighten the creep rupture strength.
  • the V content of the steel is less than 0.05 (%), the effect is insufficient.
  • the V content exceeds 0.35 (%), the ⁇ ferrite is produced which lowers the fatigue strength.
  • a range of 0.15 - 0.25 (%) is preferable.
  • the constituent Nb is an element which is very effective to enhance the high-temperature strength.
  • the element Nb is added In an excessively large amount, the coarse grains of eutectic NbC (niobium carbide) appear especially in a large-sized steel ingot, to thereby cause substantial lowering of the strength and precipitation of the ⁇ ferrite which lowers the fatigue strength. It is therefore necessary to suppress the amount of the element Nb to 0.15 (%) or below.
  • the Nb amount is less than 0.01 (%), the effect is insufficient.
  • a range of 0.02 - 0.1 (%) is preferable, and a range of 0.04 - 0.08 (%) is more preferable.
  • the constituent Ni is an element which is very effective to heighten the toughness and to prevent the production of the ⁇ ferrite.
  • the addition of the element Ni at a level of less than 0.2 (%) is unfavorable because of insufficient effects, and the addition thereof at the level of more than 1.0 (%) is also unfavorable because of degradation in the creep rupture strength.
  • a range of 0.4 - 0.8 (%) is preferable.
  • the constituent Cr is effective to improve the high-temperature strength and high-temperature oxidation resistance of the 12Cr steel.
  • a Cr content exceeding 12 (%) causes production of the deleterious 8 ferrite structure, and a Cr content below 8 (%) results in an insufficient oxidation resistance to the high-temperature high-pressure steam.
  • the addition of the element Cr is effective to enhance the creep rupture strength.
  • the Cr addition in an excessive amount causes production of the deleterious 8 ferrite structure and for lowering of the toughness.
  • a range of 8.0 - 10 (%) is preferable, and a range of 8.5 - 9.5 (%) is more preferable.
  • the constituent W (tungsten) is effective to remarkably enhance the high-temperature long-term strength of the 12Cr steel.
  • the W content of the steel should preferably be selected according to the temperature, such as 1.0 - 1.5 (%) at 620 (°C), 1.6 - 2.0 (%) at 630 (°C), 2.1 - 2.5 (%) at 640 (°C), 2.6 - 3.0 (%) at 650 (°C) and 3.1 - 3.5 (%) at 660 (°C).
  • the steel contains 1.5 -1.9 (%) of W can be used at the temperature at most 650 (°C).
  • the constituents W and Ni correlate with each other.
  • the 12Cr steel whose strength and toughness are both superior, can be obtained by setting the Ni/W ratio at 0.25 - 0.75.
  • the addition of the constituent Mo is intended to enhance the high-temperature strength.
  • the constituent W tungsten
  • the Mo addition exceeding 1.5 (%) lowers the toughness and fatigue strength of the steel. Therefore, the Mo content is recommended to be at most 1.5 (%).
  • a range of 0.4 - 0.8 (%) is preferable, and a range of 0.55 - 0.70 (%) is more preferable.
  • the addition of the constituent/constituents Ta (tantalum), Ti (titanium) or/and Zr (zirconium) is effective to heighten the toughness.
  • a sufficient effect is attained by adding at most 0.15 (%) of Ta, at most 0.1 (%) of Ti or/and at most 0.1 (%) of Zr singly or in combination.
  • the constituent Ta is added at a level of 0.1 (%) or above, the addition of the constituent Nb (niobium) can be omitted.
  • the tempered martensitic structure which is homogeneous is favorable.
  • the Cr equivalent which is computed by the formula mentioned before must be set at, at most, 10 by controlling the alloy contents.
  • the Cr equivalent when the Cr equivalent is too small, it lowers the creep rupture strength, and hence, it must be set at 4 or above.
  • a range of 6 - 9 is preferable as the Cr equivalent.
  • the addition of the constituent B (boron) remarkably enhances the high-temperature (620 (°C) or above) creep rupture strength of the steel.
  • the upper limit of the B content is set at 0.003 (%).
  • the upper limit of the B content of the large-sized casing should preferably be set at 0.0028 (%). Further, a range of 0.0005 - 0.0025 (%) is preferable, and a range of 0.001 - 0.002 (%) is particularly preferable.
  • the casing covers the high-pressure steam at temperatures of at least 620 (°C), it undergoes a high stress ascribable to the internal pressure thereof. From the viewpoint of preventing the creep rupture of the casing, therefore, the 10 5 -h creep rupture strength of at least 10 (kgf/mm 2 ) is required of the steel. Moreover, during the starting operation of the turbine, the casing undergoes a thermal stress at the time of a low metal temperature. From the viewpoint of preventing the brittle fracture of the casing, therefore, the room-temperature absorbed impact energy of at least 1 (kgf-m) is required of the steel. For the higher temperature side of the steam, the steel can be strengthened by containing at most 10 (%) of Co (cobalt).
  • the Co content should more preferably be selected from 1 - 2 (%) for 620 (°C), 2.5 - 3.5 (%) for 630 (°C), 4 - 5 (%) for 640 (°C), 5.5 - 6.5 (%) for 650 (°C), and 7 - 8 (%) for 660 (°C). But even the steel which does not contain Co can be used at each temperature.
  • the casing in an embodiment of the present invention should preferably be made of steel which satisfies at least either of conditions; a (W/Mo) ratio of 2.85 or above (preferably, 2.85 - 4.50, and more preferably, 3 - 4), and an (Mo/Cr) ratio of 0.04 - 0.08 (preferably, 0.05 - 0.06). Steel which satisfies both the conditions, is more preferable.
  • the casing material of the heat-resisting ferritic cast steel a satisfactory one can be prepared in such a way that alloying raw materials to be brought into the desired composition are melted by an electric furnace and then refined by a ladle, and that the resulting raw materials are thereafter cast into a sand mold.
  • the cast steel in which casting defects such as shrinkage holes are involved in small numbers, can be obtained by sufficiently refining and deoxidizing the raw materials before the casting.
  • the cast steel After the cast steel has been annealed at 1000 - 1150 (°C), it is normalized by heating it to 1000 -1100 (°C) and then quenching it. Subsequently, the resulting steel is tempered twice in the sequence of a temperature range of 550 - 750 (°C) and a temperature range of 670 - 770 (°C).
  • the steam turbine casing which is usable in the steam at or above 620 (°C) can be manufactured.
  • the annealing and normalizing temperatures are below 1000 (°C) carbonitrides cannot be sufficiently turned into a solid solution, and when they are excessively high, grain coarsening is caused.
  • the two tempering operations decompose retained austenite entirely, so that the steel can be rendered the tempered martensitic structure which is homogeneous.
  • the 625-°C 10 5 -h creep rupture strength of at least 10 (kgf/mm 2 ) and the room-temperature absorbed impact energy of at least 1 (kgf-m) are attained, and the prepared steel can be fabricated into the steam turbine casing which is usable in steam at or above 620 (°C).
  • the casing material in an embodiment of the present invention is set at the Cr equivalent stated before, and the ⁇ ferrite content thereof should preferably be 5 (%) or less, and more preferably 0 (%).
  • the components mentioned before should preferably be made of forged steel.
  • Fig. 1 is a sectional design view of a high-pressure steam turbine made of ferritic steel according to the present invention.
  • Fig. 2 is a sectional design view of an intermediate-pressure steam turbine made of ferritic steel according to the present invention.
  • Fig. 3 is a sectional design view of a low-pressure steam turbine according to the present invention.
  • Fig. 4 is an arrangement diagram of a coal-fired power plant according to the present invention.
  • Fig. 5 is a sectional view of a rotor shaft for the high-pressure steam turbine according to the present invention.
  • Fig. 6 is a sectional view of a rotor shaft for the intermediate-pressure steam turbine according to the present invention.
  • Fig. 7 is a graph showing the creep rupture strengths of rotor shaft and blade materials.
  • Fig. 8 is a graph showing the relationships between the creep rupture time periods and Co contents of alloys.
  • Fig. 9 is a graph showing the relationships between the creep rupture time periods and B contents of the alloys.
  • Fig. 10 is a graph showing the relationship between the creep rupture strengths and W contents of the alloys.
  • Fig. 11 is a graph showing the creep rupture strengths of casing materials.
  • Fig. 12 is a table (Table 1) exemplifying the specifications of a boiler which is operated under specified steam conditions.
  • Fig. 13 is a table (Table 2) indicating the specifications of a steam turbine which is operated under specified conditions.
  • Fig. 14 is a table (Table 3) for explaining the alloy contents of steel materials which are employed in the present invention.
  • Fig. 15 is a table (Table 4) for explaining the mechanical properties and heat treatment conditions of the steel materials which are listed in Table 3.
  • Fig. 16 is a table (Table 5) indicating the chemical constituents of welding rods which were used in buildup welding.
  • Fig. 17 is a table (Table 6) indicating those welding rods in Table 5 which were used in the respective layers of the buildup welding.
  • Fig. 18 is a table (Table 7) indicating the chemical constituents of moving blades materials according to the present invention.
  • Fig. 19 is a table (Table 8) for explaining the strengths of the rotor shaft and blade materials (in Fig. 7) according to the present invention.
  • Fig. 20 is a table (Table 9) indicating the ratios of percentages of the constituents.
  • Fig. 21 is a table (Table 10) indicating the chemical constituents of inner casing materials according to the present invention.
  • Fig. 22 is a table (Table 11) indicating the test results of the inner casing materials (in Fig. 21) according to the present invention.
  • an austenitic stainless steel pipe functioning as a superheater tube is made of a material which contains 20 - 25 (%) of Cr and 20 - 35 (%) of Ni, which contains Al and Ti in very small amounts of at most 0.5 (%), and 0.5 - 3 (%) of Mo, and which more preferably contains at most 0.5 (%) of Nb. Pulverized-coal direct firing becomes high-temperature burning.
  • the pulverized-coal fired boiler becomes larger in size as its capacity enlarges.
  • the boiler has a width of 31 (m) and a depth of 16 (m) in the class of 1050 (MW), and a width of 34 (m) and a depth of 18 (m) in the class of 1400 (MW).
  • Table 2 in Fig. 13 indicates the main specifications of a steam turbine plant which has an output of 1050 (MW) and a steam temperature of 625 (°C).
  • a cross-compound type 4-flow exhaust system is adopted, and a final-stage blade in each of the low-pressure turbines (LP's) is 43 (inches) long.
  • An HP (high-pressure turbine) - IP (intermediate-pressure turbine) connection has a rotational speed of 3600 (r/min), while the two LP's have a rotational speed of 1800 (r/min).
  • components are made of principal materials which are listed in the table.
  • the high-pressure portion (HP) undergoes the steam temperature of 625 (°C) and a pressure of 250 (kg/cm 2 ).
  • the intermediate-pressure portion (IP) has its steam heated to 625 (°C) by a reheater (R/H), and is operated under a pressure of 170 - 180 (kg/cm 2 ).
  • Fig. 1 is a sectional design view of the high-pressure steam turbine.
  • This high-pressure steam turbine is provided with a high-pressure rotor shaft 23 on which high-pressure moving blades 16 are assembled in a high-pressure inner casing 18 and a high-pressure outer casing 19 surrounding the inner casing 18.
  • the steam at the high temperature and under the high pressure as stated before is generated by the boiler explained before.
  • the generated steam is passed through a main steam pipe and then through a main steam inlet 28 defined by a flange and elbow 25, whereupon it is guided to the moving blades 16 of the double-flow first stage from a nozzle box 38.
  • the first stage has the double-flow construction, and eight other stages are disposed on one side of the high-pressure steam turbine along the rotor shaft 23.
  • the moving blades 16 are double-tenon type tangential entry dovetail blades, and the first-stage blade is about 35 (mm) long.
  • the length of the rotor shaft 23 between the centers of bearings 1 and 2 is about 5.25 (m), and the smallest diameter part of this rotor shaft corresponding to the fixed blades has a diameter of about 620 (mm), so that the ratio of the length to the diameter is about 8.5.
  • the widths of those parts of the rotor shaft 23 on which the moving blades 16 are assembled are substantially equal at the first stage and final stage, and they become smaller toward the downstream side of the steam stepwise at the five types stages, namely the first stage, second stage, third - fifth stages, sixth stage and seventh - eighth stages.
  • the axial width of the assembled part of the second stage is 0.64 times as wide as that of the assembled part of the final stage.
  • Those parts of the rotor shaft 23 which correspond to the fixed blades are smaller in diameter than those parts thereof on which the moving blades 16 are assembled.
  • the axial widths of the parts corresponding to the fixed blades become smaller stepwise from the width between the second-stage moving blade and the third-stage moving blade, to the width between the final-stage moving blade and the penultimate-stage moving blade, the latter width being 0.86 times as wide as the former width.
  • the axial widths of the parts corresponding to the fixed blades become smaller at the second - sixth stages and the sixth - ninth stages.
  • the blades and nozzles of the first stage are made of materials indicated in Table 3 of Fig. 14 to be explained later, whereas those of all the other stages are made of 12-% Cr steel which contains no W, Co or B.
  • the blade parts of the moving blades 16 in this embodiment are 35 - 50 (mm) long at the first stage, and become longer at the respective stages from the second stage toward the final stage.
  • the lengths of the blade parts of the second - final stages are set at 65 - 210 (mm), depending upon the output of the steam turbine.
  • the number of the stages is 9 - 12.
  • the lengths of the blade parts at the respective stages increase at ratios of 1.10 - 1.15 in terms of the lengths of the downstream-side blade parts adjoining the upstream-side ones, and the ratios gradually enlarge on the downstream side.
  • those parts of the rotor shaft 23 on which the moving blades 16 are assembled are larger in diameter compared with those parts thereof which correspond to the fixed blades.
  • the axial widths of the moving-blade assembled parts become larger with the lengths of the blade parts of the moving blades 16.
  • the ratios of the aforementioned axial widths to the lengths of the blade parts of the moving blades 16 are 0.65 - 0.95 at the second - final stages, and become smaller stepwise from the second stage toward the final stage.
  • the axial widths of those parts of the rotor shaft 23 which correspond to the fixed blades become smaller stepwise from the width between the second stage and the third stage, to the width between the final stage and the penultimate stage.
  • the ratios of the aforementioned axial widths to the lengths of the blade parts of the moving blades 16 are 0.7 1.7 at the second - final stages, and become smaller stepwise from the upstream-side blade part toward the downstream-side blade part.
  • the high-pressure steam turbine shown in Fig. 1 further includes a thrust bearing 5, a first shaft packing 10, a second shaft packing 11, a high-pressure spacer 14, a front bearing box 26, a journal portion 27, a high-pressure steam exhaust port 30, a reheat steam inlet 32, and a thrust-bearing wear interrupter 39.
  • Fig. 2 is a sectional view of the intermediate-pressure steam turbine.
  • This intermediate-pressure steam turbine rotates a generator (G in Fig. 13) conjointly with the high-pressure steam turbine, by the use of steam which is obtained in such a way that steam exhausted from the high-pressure steam turbine is heated again to 625 (°C) by a reheater (R/H in Fig. 13).
  • the intermediate-pressure turbine has a rotational speed of 3600 (revolutions/min).
  • the intermediate-pressure turbine includes an intermediate-pressure inner casing 21 and an outer casing 22. It is provided with fixed blades in opposition to intermediate-pressure moving blades 17.
  • the moving blades 17 have a double-flow construction of six stages, and they are disposed in a substantially symmetrical arrangement on both sides of an intermediate-pressure rotor shaft 24 in the lengthwise direction thereof.
  • the distance between the centers of bearings 3 and 4 in which the rotor shaft 24 is journaled, is about 5.5 (m).
  • the moving blade of the first stage has a length of about 92 (mm), and that of the final stage has a length of about 235 (mm).
  • the dovetail of the double-flow construction is in an inverted-chestnut shape.
  • That part of the rotor shaft 24 which corresponds to the fixed blade preceding the final-stage moving blade 17 has a diameter of about 630 (mm), and the ratio of the inter-bearing distance of this rotor shaft to the aforementioned diameter is about 8.7.
  • the axial widths of those parts of the rotor shaft 24 of the intermediate-pressure steam turbine of this embodiment on which the moving blades 17 are assembled become larger toward the downstream side of the steam stepwise at the three sorts of stages of the first stage, the fourth and fifth stages and the final stage.
  • the axial width of the assembled part of the final stage is about 1.4 times as large as that of the assembled part of the first stage.
  • those parts of the rotor shaft 24 of the intermediate-pressure steam turbine which correspond to the fixed blades are smaller in diameter than those parts thereof on which the moving blades 17 are assembled.
  • the axial widths of the parts corresponding to the fixed blades become smaller toward the downstream side of the steam stepwise at the four moving-blade stages of the first stage, second stage, third stage and final stage, and the axial width at the final stage is about 0.7 time as large as the axial width at the first stage.
  • the blades and nozzles of the first stage are made of the materials indicated in Table 3 of Fig. 14 to be explained later, whereas those of all the other stages are made of the 12-% Cr steel which contains no W, Co or B.
  • the blade parts of the moving blades 17 in this embodiment become longer at the respective stages from the first stage toward the final stage.
  • the lengths of the blade parts of the first - final stages are set at 90 - 350 (mm), preferably 100 - 300 (mm), depending upon the output of the steam turbine.
  • the number of the stages is 6 - 9.
  • the lengths of the blade parts at the respective stages increase at ratios of 1.1 - 1.2 in terms of the lengths of the downstream-side blade parts adjoining the upstream-side ones.
  • those parts of the rotor shaft 24 on which the moving blades 17 are assembled are larger in diameter compared with those parts thereof which correspond to the fixed blades.
  • the axial widths of the moving-blade assembled parts become larger with the lengths of the blade parts of the moving blades 17.
  • the ratios of the aforementioned axial widths to the lengths of the blade parts of the moving blades 17 are 0.5 - 0.7 at the first - final stages, and become smaller stepwise from the first stage toward the final stage.
  • the axial widths of those parts of the rotor shaft 24 which correspond to the fixed blades become smaller stepwise from the width between the first stage and the second stage, to the width between the final stage and the penultimate stage.
  • the ratios of the aforementioned axial widths to the lengths of the blade parts of the moving blades 17 are 0.5 - 1.5, and become smaller stepwise from the upstream-side blade part toward the downstream-side blade part.
  • the intermediate-pressure steam turbine shown in Fig. 2 further includes shaft packings 12 and 13, an intermediate-pressure spacer 15, a first inner casing 20 (associated with the second inner casings 21), reheat steam inlets 29, steam exhaust ports 30, crossover pipes 31, and a warming steam inlet 40.
  • Fig. 3 is a sectional view of the low-pressure turbine. Two low-pressure turbines are connected in tandem, and they have the same design.
  • Moving blades 41 are provided as eight stages on both sides of a rotor shaft 44 in the lengthwise direction thereof, and these moving blades on both sides are substantially in a bilaterally symmetric arrangement.
  • fixed blades 42 are disposed in correspondence with the moving blades 41.
  • the moving blade 41 of the final stage is 1,092.2 (mm) (43 (inches)) long, and is made of a Ti-based alloy.
  • the moving blades 41 of all the stages are double-tenon type tangential entry dovetail blades.
  • a nozzle box 45 is of double-flow type.
  • the Ti-based alloy is subjected to age hardening, and it contains 6 (%) of Al and 4 (%) of V in terms of weight.
  • the rotor shafts 44 are made of forged steel of fully-tempered bainitic structure prepared from superclean materials (high purity materials) which consist of 3.75 (%) of Ni, 1.75 (%) of Cr, 0.4 (%) of Mo, 0.15 (%) of V, 0.25 (%) of C, 0.05 (%) of Si, 0.10 (%) of Mn, and the balance of Fe. All the moving blades and the fixed blades except the final-stage ones are made of 12-% Cr steel containing 0.1 (%) of Mo. Cast steel containing 0.25 (%) of C is employed as the material of the inner and outer casings.
  • the distance between the centers of bearings 43 in this embodiment is 7500 (mm).
  • Those parts of the rotor shaft 44 which correspond to the fixed blades 42 have a diameter of about 1280 (mm), while those parts thereof on which the moving blades 41 are assembled have a diameter of about 2275 (mm).
  • the ratio of the inter-bearing distance to the smaller diameter of the rotor shaft 44 is about 5.9.
  • the axial widths of the moving-blade assembled parts of the rotor shaft 44 gradually enlarge at the five sorts of stages of the first - third stages, the fourth stage, the fifth stage, the sixth - seventh stages and the eighth stage.
  • the width of the final stage is about 2.5 times as large as that of the first stage.
  • those parts of the rotor shaft 44 which correspond to the fixed blades 42 are smaller in diameter than those parts thereof on which the moving blades 41 are assembled.
  • the axial widths of the parts corresponding to the fixed blades 42 become larger toward the downstream side of the steam gradually at the three sorts of moving-blade stages of the first stage, the fifth - sixth stages and the seventh stage, and the width at the final stage is about 1.9 times as large as the width at the first stage.
  • the blade parts of the moving blades 41 in this embodiment become longer at the respective stages from the first stage toward the final stage.
  • the lengths of the blade parts of the first - final stages are set at 90 - 1270 (mm), depending upon the output of the steam turbine.
  • the number of the stages is 8
  • the lengths of the blade parts at the respective stages enlarge at ratios of 1.3 - 1.6 in terms of the lengths of the downstream-side blade parts adjoining the upstream-side ones.
  • those parts of the rotor shaft 44 on which the moving blades 41 are assembled are larger in diameter compared with those parts thereof which correspond to the fixed blades 42.
  • the axial widths of the moving-blade assembled parts become larger with the lengths of the blade parts of the moving blades 41.
  • the ratios of the aforementioned axial widths to the lengths of the blade parts of the moving blades 41 are 0.15 - 0.91 at the first - final stages, and become smaller stepwise from the first stage toward the final stage.
  • the axial widths of those parts of the rotor shaft 44 which correspond to the fixed blades 42 become smaller stepwise from the width between the first stage and the second stage, to the width between the final stage and the penultimate stage.
  • the ratios of the aforementioned axial widths to the lengths of the blade parts of the moving blades 41 are 0.25 - 1.25, and become smaller stepwise from the upstream-side blade part toward the downstream-side blade part.
  • Fig. 4 is a diagram showing the typical plant layout of a coal-fired high-temperature high-pressure steam turbine plant.
  • the high-temperature high-pressure steam turbine plant in this embodiment is chiefly configured of a coal-fired boiler 51, a high-pressure turbine 52, an intermediate-pressure turbine 53, low-pressure turbines 54 and 55, steam condensers 56, condensate pumps 57, a low-pressure feed water heater system 58, a deaerator 59, a pressuring pump 60, a boiler feed pump 61 and a high-pressure feed water heater system 63.
  • ultra-supercritical steam generated by the boiler 51 enters the high-pressure turbine 52 to generate power.
  • exhaust steam from the high-pressure turbine 52 is reheated by the boiler 51, and the resulting steam enters the intermediate-pressure turbine 53 to generate power again.
  • Exhaust steam from the intermediate-pressure turbine 53 enters the low-pressure turbines 54 and 55 to generate power, and it is thereafter condensed by the condensers 56.
  • the resulting condensate is sent to the low-pressure feed water heater system 58 and deaerator 59 by the condensate pumps 57.
  • Feed water deaerated by the deaerator 59 is sent by the pressurizing pump 60 and boiler feed pump 61 to the high-pressure feed water heater system 63, in which the water is heated and from which it is returned to the boiler 51.
  • the feed water is turned into high temperature and high pressure steam by passing through an economizer 64, a vaporizer 65 and a superheater 66.
  • the combustion gas of the boiler 51 having heated the steam comes out of the economizer 64, and it thereafter enters an air heater 67 to heat air.
  • the boiler feed pump 61 is driven by a boiler feed pump driving turbine which is operated by steam extracted from the intermediate-pressure turbine 53.
  • the temperature of the feed water having emerged from the high-pressure feed water heater system 63 is much high erthan a feed water temperature in the prior-art thermal power plant, and hence, the temperature of the combustion gas having emerged from the economizer 64 disposed in the boiler 51 becomes much higher than in the prior-art boiler as an inevitable consequence. Therefore, heat is recovered from the exhaust gas of the boiler 51 so as to prevent the gas temperature from lowering.
  • Numerals 68 in Fig. 4 indicate generators which are respectively joined to the HP - IP connection and the tandem LP connection.
  • the generator shaft should preferably be made of steel of fully-tempered bainitic structure which contains 0.15 - 0.30 (%) of C, 0.1 - 0.3 (%) of Si, at most 0.5 (%) of Mn, 3.25 - 4.5 (%) of Ni, 2.05 - 3.0 (%) of Cr, 0.25 - 0.60 (%) of Mo and 0.05 - 0.20 (%) of V, and which has a room-temperature tensile strength of 93 (kg/mm 2 ) or above, particularly 100 (kg/mm 2 ) or above, and a 50% FATT (Fracture Appearance Transition Temperature) of 0 (°C) or below, particularly -20 (°C) or below.
  • FATT Frracture Appearance Transition Temperature
  • the steel should preferably be such that a magnetizing force at 21.2 (kG) is at most 985 (AT/cm), that impurities P, S, Sn, Sb and As contained is at the total amount of most 0.025 (%), and that a ratio Ni/Cr is at most 2.0.
  • Figs. 5 and 6 are front views showing examples of the high-pressure and intermediate-pressure turbine rotor shafts, respectively.
  • the exemplified high-pressure turbine shaft has a construction which consists of a multistage side and a single-stage side, and in which blades totaling eight stages are assembled on both sides so as to laterally center on the first-stage blade of the multistage side.
  • the exemplified intermediate-pressure turbine shaft has a construction in which multistage blades are assembled in a bilaterally symmetric arrangement so as to total six stages on each side and to be substantially bounded by the laterally central part of this shaft.
  • the rotor shaft for each low-pressure turbine is not specifically exemplified, the rotor shaft of any of the high-pressure, intermediate-pressure and low-pressure turbines is formed with a center hole, through which the presence of defects is examined by a ultrasonic test, a visual test and a fluorescent penetrant inspection.
  • numerals 27 in each of Figs. 5 and 6 denote the journal parts of the corresponding rotor shaft.
  • Table 3 in Fig. 14 indicates the chemical constituents (weight-%) which were used for the principal components of the high-pressure turbine, intermediate-pressure turbine and low-pressure turbines in an example of this embodiment.
  • all the high-temperature parts of the high-pressure and intermediate-pressure turbines were made of the steel materials of ferritic crystalline structure which had a coefficient of thermal expansion of 12 ⁇ 10 -6 (/°C), so that no problems ascribable to discrepancy in the coefficients of thermal expansion occurred.
  • an electrode was prepared in such a way that the heat-resisting cast steel mentioned in Table 3 was melted in an amount of 30 (tons) by an electric furnace, that the molten steel was subjected to carbon vacuum deoxidation and then poured into a metal mold, and that the molded steel was forged. Further, the electrode was subjected to electroslag remelting so as to melt from the upper part of the cast steel to the lower part thereof, and the resulting steel was forged into a rotor shape having a maximum diameter of 1050 (mm) and a length of 5700 (mm). The forging was carried out at temperatures of at most 1150 (°C) in orderto prevent any forging cracks.
  • the forged steel was annealed, it was heated to 1050 (°C) and was subjected to water spray quenching. Subsequently, the resulting steel was tempered twice at temperatures of 570 (°C) and 690 (°C), and it was machined into the shape shown in Fig. 5 or Fig. 6.
  • the upper part side of the electroslag ingot was used as the first-stage blade side of the rotor shaft, and the lower part side as used as the final-stage blade side.
  • the heat-resisting steel materials also mentioned in Table 3 of Fig. 14 were melted by a vacuum arc furnace, and they were forged and molded into the shapes of blade and nozzle blanks each having a width of 150 (mm), a height of 50 (mm) and a length of 1000 (mm).
  • the forging was carried out at temperatures of at most 1150 (°C) in order to prevent any forging cracks.
  • the forged steel was heated to 1050 (°C), subjected to oil quenching and tempered at 690 (°C). Subsequently, the resulting steel was machined into the predetermined shapes.
  • a preheating temperature, an inter-pass temperature and a post-heating starting temperature were set at 200 (°C), and a post-heating treatment was conducted at 400 (°C) for 30 (minutes). No welding cracks were noted in either of the materials of the present invention, and the weldability was good.
  • Table 4 shown in Fig. 15 indicates the heat treatment conditions of the ferritic steel materials listed in Table 3 of Fig. 14, and the mechanical properties of the principal members of the high-temperature steam turbines made of the materials as tested by cutting these members.
  • Fig. 7 is a graph showing the relationships between the 105-h creep rupture strength and temperature for different rotor shaft materials. It has been found that the materials according to the present invention satisfy the requirements, which the 10 5 -h creep rupture strength is equal to or stronger than 13kg/mm 2 , at 610 - 640 (°C). Incidentally, the 12Cr rotor material is the prior-art material which contains no B, W or Co.
  • bearing characteristics were improved in such a way that Cr - Mo low-alloy steel was deposited on each journal portion of the rotor shaft by buildup welding.
  • the buildup welding was carried out as stated below.
  • Welding rods employed in the buildup welding were shielded-arc ones having diameters of 4.0 (mm).
  • Table 5 shown in Fig. 16 indicates the chemical constituents (weight-%) of deposited metals which were formed by the welding operations with the shielded-arc welding rods.
  • the constituents of the deposited metals were substantially the same as those of the corresponding weld metals (which shall be called the "welding rods A - D" below).
  • the conditions of the buildup welding were a welding current of 170 (A), a voltage of 24 (V) and a rate of 26 (cm/min).
  • a preheating temperature, an inter-pass temperature and a stress-relief-annealing (SR) starting temperature were 250 - 350 (°C), and the SR was conducted by holding the deposited layers at 630 (°C) for 36 (hours).
  • Table 7 in Fig. 18 lists the chemical constituents of the Ni-based precipitation-strengthened alloys each of which was applied to the first - third stages of the moving blades in the high-pressure turbine and the first stage of the moving blades in the intermediate-pressure turbine.
  • each of these alloys was produced in such a way that an ingot was prepared by vacuum arc remelting, followed by hot forging, that the hot-forged ingotwas subsequently heated at 1,070 - 1,200 (°C) for 1 - 8 (hours)
  • the alloy composition of the pertinent alloy as a treatment for turning the ingot into a solid solution, followed by air cooling, and that the air-cooled material was heated at 700 - 870 (°C) for 4 - 24 (hours) as an ageing treatment.
  • Table 9 of Fig. 20 indicates the ratios of percentages of the constituents.
  • each of the alloys was quenched under the conditions of 1050 (°C) ⁇ 5 (hours) and 100 (°C/h) cooling and was subjected to primary tempering of 570 (°C) ⁇ 20 (hours) and the secondary tempering of 690 (°C) ⁇ 20 (hours), by simulating the central part of the rotor shaft.
  • each alloy was quenched under the condition of 1100 (°C) ⁇ 1 (hour) and was tempered under the condition of 750 (°C) ⁇ 1 (hour). Thereafter, the creep rupture tests of such alloys were executed under the conditions of 625 (°C) and 30 (kgf/mm 2 ). The results obtained are also listed in Table 8 of Fig. 19.
  • the comparative alloy No. 10 does not contain Co unlike the alloys of the present invention.
  • Figs. 8 and 9 are graphs showing those influences of the Co content and B content of the alloys (listed in Table 8 of Fig. 19) which are respectively exerted on the creep rupture strength.
  • the creep rupture time period of the alloy becomes longer with increase in the Co content.
  • the increase of the Co content by a large amount is unfavorable for the reason that the alloy is liableto become brittle when heated at 600-660 (°C).
  • the Co content should preferably be 2 - 5 (%) for 620 - 630 (°C) and 5.5 - 8 (%) for 630 - 660 (°C) .
  • the strength of the alloy is prone to lower with increase in the B content. It is understood that the alloy exhibits a superior strength when the B content is 0.03 (%) or below.
  • the strength is increased by setting the B contentto 0.001 - 0.01 (%) and the Co content to 2 - 4 (%) in a temperature range of 620 - 630 (°C), and by increasing the B content to 0.01 - 0.03 (%) and the Co content to 5 - 7.5 (%) on a higher temperature side of 630 - 660 (°C).
  • the alloy is strengthened more by a lower N content at the temperatures exceeding 600 (°C) in this embodiment. This is also apparent from the fact that sample No. 2 in Table 8 of Fig. 19 exhibits a higher strength than sample No. 8 having a higher N content.
  • the N content of the alloy should preferably be 0.01 - 0.04 (%). Since the constituent N was hardly contained by the vacuum melting, the parent alloy was doped with the element N.
  • Embodiment 1 It is seen from Fig. 7 concerning Embodiment 1 that all the alloys according to the present invention as listed in Table 8 exhibit high strengths.
  • the rotor material indicated in Embodiment 1 corresponds to the alloy of the sample No. 2 in this embodiment.
  • the sample No. 8 having a low Mn content of 0.09 (%) exhibits a higher strength, subject to equal Co contents.
  • the Mn content of the alloy should preferably be set at 0.03 - 0.20 (%) in order to attain a higher strength.
  • Table 10 shown in Fig. 21 indicates chemical constituents (weight-%) which concern the inner casing materials of the present invention.
  • the ingot of each of the listed samples was prepared in such a way that each alloy was melted in an amount of 200 (kg) by a highfrequency induction furnace, and that the molten alloy was poured into a sand mold having a maximum thickness of 200 (mm), a width of 380 (mm) and a height of 440 (mm).
  • the samples Nos. 3 - 7 are materials according to the present invention, whereas the samples Nos. 1 and 2 are materials of the prior art.
  • the weldability of each of the samples was evaluated in conformity with "JIS Z3158".
  • a preheating temperature, an inter-pass temperature and a post-heating starting temperature were set at 150 (°C), and a post-heating treatment was conducted at 400 (°C) for 30 (minutes).
  • Table 11 shown in Fig. 21 indicates the test results of the samples Nos. 1 - 7 listed in Table 10 of Fig. 21, concerning tensile characteristics at room temperature, V-notch Charpy impact absorption energy at 20 (°C), a 650-°C 10 5 -h creep rupture strength, and a welding crack.
  • each of the materials of the present invention (samples Nos. 3, 4, 6 and 7) doped with appropriate amounts of B, Mo and W, fully satisfy the special qualities (625-°C 10 5 -h strength ⁇ 8 kgf/mm 2 , and 20-°C absorbed impact energy ⁇ 1 kg-m) required of the high-temperature high-pressure turbine casing.
  • the samples Nos. 3, 6 and 7 exhibit high strengths exceeding 9 (kgf/mm 2 ).
  • none of the materials of the present invention (except the sample No. 3) suffer from welding cracks and all have good weldability.
  • the Ni/W ratio of the alloy is controlled to 0.25 - 0.75, thereby obtaining the casing material of the heat-resisting cast steel which meets a 625 °C 10 5 -h creep rupture strength of at least 9 (kgf/mm 2 ) and a room-temperature absorbed impact energy of at least 1 (kgf-m) that are required of the high-pressure and intermediate-pressure inner casings, and main-steam stop valve and control valve casings of the high-temperature high-pressure turbine under a pressure of at least 250 (kgf/cm 2 ) at a temperature of 621 (°C).
  • the W content and the Ni/W ratio are respectively controlled to 1.2 - 2 (%) and 0.25 - 0.75, thereby obtaining the excellent casing material of the heat-resisting cast steel which meets a 625-°C 10 5 -h creep rupture strength of at least 10 (kgf/mm 2 ) and a room-temperature absorbed impact energy of at least 2 (kgf-m).
  • Fig. 10 is a graph showing the relationship between the W content and the creep rupture strength for the alloys explained above. As indicated in the figure, when the W content is at least 1.0 (%), the strength is remarkably increased, and a value of at least 8.0 (kg/mm 2 ) is attained, especially for a W content of at least 1.5 (%).
  • Fig. 11 is a graph showing the relationship between the 10 5 -hour creep rupture strength and the rupture temperature for the alloys explained above.
  • the alloy of the sample No. 7 in the present invention satisfactorily meets the required strength at temperatures of, at most, 640 (°C).
  • alloying raw materials to be brought into the desired composition of the heat-resisting cast steel in the present invention were melted in an amount of 1 (ton) by an electric furnace and then refined by a ladle, and the resulting raw materials were thereafter poured into a sand mold.
  • the inner casing for the high-pressure portion or intermediate-pressure portion as described in Embodiment 1 was obtained.
  • the manufactured casing fully satisfies the special qualities (625-°C 10 5 -h strength ⁇ 9 kgf/mm 2 , and 20-°C absorbed impact energy ⁇ 1 kg-m) required of the casing of the high-temperature high-pressure turbine of 250 (atm.) and 625 (°C), and that it can be subjected to welding.
  • This embodiment sets the steam temperature of a high-pressure steam turbine and an intermediate-pressure steam turbine at 649 (°C) in place of 625 (°C) in Embodiment 1, and the construction and size thereof are obtained by substantially the same design as in Embodiment 1.
  • Different here from Embodiment 1 are the rotor shafts, first-stage moving blades, first-stage fixed blades and inner casings of the high-pressure and intermediate-pressure steam turbines that come into direct contact with the steam of the above temperature.
  • the B content and the Co content are respectively increased to 0.01 - 0.03 (%) and 5 - 7 (%) in the foregoing materials listed in Table 8 of Fig. 19.
  • the W content of the material in Embodiment 1 as indicated in Table 3 of Fig. 14 is increased to 2 - 3 (%), and Co is added 3 (%).
  • the design in the prior art can be used very meritoriously. More specifically, in this embodiment, the design concept in the prior art as it is can be used in the point that all the structural materials to be exposed to the high temperature are formed of ferritic steel.
  • the material used for the first stage in Embodiment 1 should preferably be employed for these components.
  • the steam temperature of low-pressure steam turbines in this embodiment becomes about 405 (°C) which is somewhat higher than about 380 (°C) in Embodiment 1.
  • the same superclean material high purity material
  • a turbine configuration in this embodiment is of the cross-compound type
  • the tandem type in which all the turbines are directly connected can also be realized at a rotational speed of 3600 (r.p. m.).
  • heat-resisting martensitic cast steel the creep rupture strength and room-temperature toughness of which are high at 610 - 660 (°C). Therefore, all principal members for ultra-supercritical pressure turbines at individual temperatures can be made of heat-resisting ferritic steel, the basic designs of prior-art steam turbines can be used as they are, and a thermal power plant of high reliability can be built.
  • the high-temperature steam turbine made entirely of the ferritic steel according to the present invention does not use the austenitic alloy which has a large coefficient of thermal expansion. Therefore, the steam turbine has such advantages as being rapidly started with ease and being less susceptible to thermal fatigue damage.

Landscapes

  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Materials Engineering (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Turbine Rotor Nozzle Sealing (AREA)

Claims (30)

  1. Dampfturbine mit einem Rotorschaft (23, 24), auf dem Rotorschaft angebrachten beweglichen Blättern (16, 17), feststehenden Blättern, die einen Dampf-Zustrom zu den beweglichen Blättern (16, 17) leiten, und einem die feststehenden Blätter haltenden Innengehäuse (18; 20, 21), wobei
       der Dampf bei einer Temperatur von 610 bis 660 °C in eine erste Stufe der beweglichen Blätter (16, 17) strömt,
       Teile der Turbine aus einem wärmebeständigen ferritischen Stahl mit 9 bis 13 Gew. % Cr hergestellt sind,
       die beweglichen Blätter (16, 17), die feststehenden Blätter und das Innengehäuse (18; 20, 22) aus martensitischem Stahl mit 8 bis 13 Gew. % Cr hergestellt sind,
       der Rotorschaft (23, 24) aus hochfestem martensitischen Stahl mit voll getemperter martensitischer Struktur hergestellt ist, der eine 105-Stunden-Zeitstandfestigkeit von mindestens 15 kg/mm2 bei einer der genannten Dampftemperatur entsprechenden Temperatur zeigt und der 9 bis 13 Gew. % Cr, 0,05 - 0,20 % C, maximal 0,15 % Si, 0,03 - 1,5 % Mn, 0,05 - 1,0 % Ni, 0,05 - 0,35 % V, 0,01 - 0,20 % Nb, 0,01 - 0,06 % N, 0,05 - 0,5 % Mo, 1,0 - 3,5 % W enthält und mindestens 78 % Fe aufweist, wobei die Prozent-Angaben auf das Gewicht bezogen sind,
       dadurch gekennzeichnet, daß
       der hochfeste martensitische Stahl des Rotorschafts (23, 24)
       zur Verwendung bei einer Dampftemperatur von 610 bis 630 °C 2 - 5 % Co und 0,0005 - 0,01 % B und
       zur Verwendung bei einer Dampftemperatur von 630 bis 660 °C 5 - 10 % Co und 0,01 - 0,03 % B
       enhält, wobei die Prozent-Angaben auf das Gewicht bezogen sind.
  2. Dampfturbine nach Anspruch 1, wobei das Innengehäuse (18; 20, 21) aus martensitischem Stahl hergestellt ist, der eine 105-Stunden-Zeitstandfestigkeit von mindestens 10 kg/mm2 bei einer der Temperatur des zuströmenden Dampfs entsprechenden Temperatur zeigt.
  3. Dampfturbine nach Anspruch 1 oder 2, wobei die beweglichen Blätter (16, 17) und/oder die feststehenden Blätter mindestens der ersten Stufe aus martensitischem Stahl hergestellt sind, der eine 105-Stunden-Zeitstandfestigkeit von mindestens 15 kg/mm2 bei einer der Temperatur des zuströmenden Dampfs der ersten Stufe entsprechenden Temperatur zeigt oder bei Raumtemperatur eine Gegenspannung von mindestens 90 kg/mm2 zeigt.
  4. Dampfturbine nach Anspruch 1 oder 2, wobei unter den beweglichen Blättern (16, 17) die Blätter der ersten Stufe aus einer auf Nickel beruhenden abgeschiedenen Verstärkungslegierung hergestellt sind, die bei Raumtemperatur eine Gegenspannung von mindestens 100 kg/mm2 zeigt.
  5. Dampfturbine nach einem der Ansprüche 1 bis 4, wobei
       das Innengehäuse (18; 20, 21) aus einem hochfesten martensitischen Stahl hergestellt ist, der 0,06 - 0,16 % C, maximal 0,5 % Si, maximal 1 % Mn, 0,2 - 1,0 % Ni, 8 - 12 % Cr, 0,05 - 0,35 % V, 0,01 - 0,15 % Nb, 0,01 - 0,1 % N, maximal 1,5 % Mo, 1 - 4 % W und 0,0005 - 0,03 % B enthält und mindestens 85 % Fe aufweist, wobei die Prozent-Angaben auf das Gewicht bezogen sind.
  6. Dampfturbine nach einem der Ansprüche 1 bis 5 zur Verwendung in Hochdruck-Anwendungen, wobei die beweglichen Blätter (16) mit Ausnahme einer ersten Doppelstrom-Stufen in mindestens 7 Stufen auf jeder Seite in Längsrichtung des Rotorschafts (23) angeordnet sind und der Rotorschaft (23) zwischen der jeweiligen Mitte von Lagern, in denen er wellengelagert ist, einen Abstand (L) von mindestens 5000 mm und an seinen Teilen, die den feststehenden Blättern entsprechen, einen Minimalduchmesser (D) von mindestens 600 mm aufweist, wobei das Verhältnis (L/D) zwischen dem Abstand (L) und dem Durchmesser (D) 8,0 - 9.0 beträgt.
  7. Dampfturbine nach einem der Ansprüche 1 bis 5 zur Verwendung in Mitteldruck-Anwendungen, wobei die beweglichen Blätter (17) einen Doppelstrom-Aufbau aufweisen, bei dem auf jeder Seite in Längsrichtung des Rotorschafts (24), in wechselweise symmetrischer Anordnung auf beiden Seiten, 6 Stufen enthalten sind und bei dem die ersten Stufen der Anordnung auf einem Mittelteil des Rotorschafts (24) in Längsrichtung angebracht sind; wobei der Rotorschaft (24) zwischen der jeweiligen Mitte von Lagern, in denen er wellengelagert ist, einen Abstand (L) von mindestens 5000 mm und an seinen Teilen, die den feststehenden Blättern entsprechen, einen Minimalduchmesser (D) von mindestens 600 mm aufweist, wobei das Verhältnis (L/D) zwischen dem Abstand (L) und dem Durchmesser (D) 8,2 - 9.2 beträgt.
  8. Dampfturbine nach einem der Ansprüche 1 bis 6 zur Verwendung in Hochdruck-Anwendungen, wobei die beweglichen Blätter (16) so in mindestens 7 Stufen angeordnet sind, daß die jeweilige Länge der beweglichen Blätter von einer stromaufwärts-Seite des Dampfstroms zu dessen stromabwärts-Seite länger wird, wobei eine erste Stufe der beweglichen Blätter nicht kürzer als 35 mm und eine letzte Stufe der beweglichen Blätter nicht länger als 210 mm ist; wobei die Durchmesser derjenigen Teile des Rotorschafts (23), auf denen die beweglichen Blätter angebracht sind, größer als die Durchmesser derjenigen Teile des Rotorschafts (23) sind, die den feststehenden Blättern entsprechen; und wobei in Axialrichtung des Rotorschafts (23) die jeweilige Weite der entsprechenden Stufen der Teile des Rotorschafts zur Anbringung der beweglichen Blätter auf einer stromabwärts-Seite größer als auf einer stromaufwärts-Seite ist und die Verhältnisse dieser Weiten zu den Längen der beweglichen Blätter innerhalb eines Bereichs von 0,6 - 1,0 auf der stromabwärts-Seite kleiner als auf der stromaufwärts-Seite sind.
  9. Dampfturbine nach einem der Ansprüche 1 bis 6 oder 8 zur Verwendung in Hochdruck-Anwendungen, wobei die beweglichen Blätter (16) so in mindestens 7 Stufen angeordnet sind, daß die jeweilige Länge der beweglichen Blätter von einer stromaufwärts-Seite des Dampfstroms zu dessen stromabwärts-Seite länger wird, wobei eine erste Stufe der beweglichen Blätter (16) nicht kürzer als 35 mm und eine letzte Stufe der beweglichen Blätter (16) nicht länger als 210 mm ist; wobei die Verhältnisse zwischen den Längen der beweglichen Blätter der jeweils benachbarten Stufen maximal 1,2 betragen und diese Verhältnisse auf der stromabwärts-Seite größer als auf der stromaufwärts-Seite sind.
  10. Dampfturbine nach einem der Ansprüche 1 bis 6, 8 oder 9 zur Verwendung in Hochdruck-Anwendungen, wobei die beweglichen Blätter (16) in mindestens 7 Stufen so angeordnet sind, daß die jeweilige Länge der beweglichen Blätter von einer stromaufwärts-Seite des Dampfstroms zu dessen stromabwärts-Seite länger wird, wobei eine erste Stufe der beweglichen Blätter nicht kürzer als 35 mm und eine letzte Stufe der beweglichen Blätter nicht länger als 210 mm ist; wobei die Durchmesser derjenigen Teilen des Rotorschafts (23) die den feststehenden Blättern entsprechen, kleiner als die Durchmesser der Abschnitte zur Anbringung der beweglichen Blätter sind und die in Axialrichtung des Rotorschafts genommene jeweilige Weite derjenigen Teile des Rotorschafts (23), die den feststehenden Blättern entsprechen, auf der stromabwärts-Seite kleiner als auf der stromaufwärts-Seite ist und die Verhältnisse dieser Weiten zu den Längen der stromabwärts-seitigen beweglichen Blätter (16) des entsprechenden Abschnitts innerhalb eines Bereichs von 0,65 - 1,8 zur stromabwärts-Seite hin abnehmen.
  11. Dampfturbine nach einem der Ansprüche 1 bis 5 oder 7 zur Verwendung in Mitteldruck-Anwendungen, wobei die beweglichen Blätter (17) einen Doppelstrom-Aufbau aufweisen, bei dem auf jeder von zwei Seiten in Längsrichtung des Rotorschafts (24), in wechselweise symmetrischer Anordnung auf beiden Seiten, mindestens 6 Stufen enthalten sind und die jeweilige Länge der beweglichen Blätter von einer stromaufwärts-Seite des Dampfstroms zu dessen stromabwärts-Seite länger wird, wobei eine erste Stufe der beweglichen Blätter (17) nicht kürzer als 90 mm und eine letzte Stufe der beweglichen Blätter (17) nicht länger als 350 mm ist; wobei die Durchmesser derjenigen Teile des Rotorschafts (24), auf denen die beweglichen Blätter (17) angebracht sind, größer als die Durchmesser derjenigen Teile des Rotorschafts sind, die den feststehenden Blättern entsprechen; und wobei in Axialrichtung des Rotorschafts die jeweilige Weite der Teile des Rotorschafts zur Anbringung der beweglichen Blätter auf der stromabwärts-Seite größer als auf der stromaufwärts-Seite ist und die Verhältnisse dieser Weiten zu den Längen der beweglichen Blätter innerhalb eines Bereichs von 0,45 - 0,75 von der stromaufwärts-Seite zur stromabwärts-Seite abnehmen.
  12. Dampfturbine nach einem der Ansprüche 1 bis 5, 7 oder 11 zur Verwendung in Mitteldruck-Anwendungen, wobei die beweglichen Blätter (17) einen Doppelstrom-Aufbau aufweisen, bei dem auf jeder von zwei Seiten in Längsrichtung des Rotorschafts (24), in wechselweise symmetrischer Anordnung auf beiden Seiten, mindestens 6 Stufen enthalten sind und die jeweilige Länge der beweglichen Blätter von einer stromaufwärts-Seite des Dampfstroms zu dessen stromabwärts-Seite länger wird, wobei eine erste Stufe der beweglichen Blätter nicht kürzer als 90 mm und eine letzte Stufe der beweglichen Blätter nicht länger als 350 mm ist; und wobei die Längen der entsprechenderweise benachbarten beweglichen Blätter auf der stromabwärts-Seite größer als auf der stromaufwärts-Seite sind und die Verhältnisse der Längen benachbarter Blätter maximal 1,3 betragen und zur stromabwärts-Seite stetig zunehmen.
  13. Dampfturbine nach einem der Ansprüche 1 bis 5 oder 7, 11 oder 12 zur Verwendung in Mitteldruck-Anwendungen, wobei die beweglichen Blätter (17) einen Doppelstrom-Aufbau aufweisen, in dem auf jeder von zwei Seiten in Längsrichtung des Rotorschafts (24), in wechselweise symmetrischer Anordnung auf beiden Seiten, mindestens 6 Stufen vorhanden sind und die jeweilige Länge der beweglichen Blätter (17) von einer stromaufwärts-Seite des Dampfstroms zu dessen stromabwärts-Seite länger wird, wobei eine erste Stufe der beweglichen Blätter nicht kürzer als 90 mm und eine letzte Stufe der beweglichen Blätter nicht länger als 350 mm ist; wobei die Durchmesser derjenigen Teile des Rotorschafts (24), die den feststehenden Blättern entsprechen, kleiner als die Durchmesser des Abschnitts des Rotorschafts zur Anbringung der beweglichen Blätter sind und die jeweilige in Axialrichtung des Rotorschafts genommene Weite derjenigen Teile des Rotorschafts (24), die den feststehenden Blättern entsprechen, auf der stromabwärts-Seite kleiner als auf der stromaufwärts-Seite ist und die Verhältnisse dieser Weiten zu den Längen der stromabwärts-seitigen beweglichen Blätter des entsprechenden Abschnitts innerhalb eines Bereichs von 0,45 - 1,60 zur stromabwärts-Seite hin abnehmen.
  14. Dampfturbine nach einem der Ansprüche 1 bis 6, 8 bis 10 zur Verwendung in Hochdruck-Anwendungen, wobei die beweglichen Blätter (16) in mindestens 7 Stufen angeordnet sind; wobei die Durchmesser derjenigen Teile des Rotorschafts (23) die den feststehenden Blättern entsprechen, kleiner als die Durchmesser derjenigen Teile des Rotorschafts sind, die den angebrachten beweglichen Blättern entsprechen; wobei in Axialrichtung des Rotorschafts die jeweilige Weite der Rotorschaftsteile, die den feststehenden Blättern entsprechen, bei mindestens zwei der Stufen auf einer stromaufwärts-Seite des Dampfstroms schrittweise größer als auf dessen stromabwärts-Seite ist und die Weite zwischen der letzten Stufe der beweglichen Blätter (16) und der der letzten Stufe direkt vorhergehenden Stufe 0,75 - 0,95 mal so groß wie die Weite zwischen der zweiten Stufe und der dritten Stufe der beweglichen Blätter ist; und wobei in Axialrichtung des Rotorschafts die jeweilige Weite der Rotorschaftsteile, die den angebrachten beweglichen Blättern entsprechen, bei mindestens drei der Stufen auf der stromabwärts-Seite des Dampfstroms schrittweise größer als auf dessen stromaufwärts-Seite ist und die axiale Weite der letzten Stufe der beweglichen Blätter (16) am Abschnitt zur Anbringung der beweglichen Blätter 1 bis 2 mal so groß wie die axiale Weite der zweiten Stufe der beweglichen Blätter (16) bei dem Abschnitt zur Anbringung der beweglichen Blätter ist.
  15. Dampfturbine nach einem der Ansprüche 1 bis 5, 7, 11 bis 13 zur Verwendung in Mitteldruck-Anwendungen, wobei die beweglichen Blätter (17) in mindestens 6 Stufen angeordnet sind; wobei die Durchmesser derjenigen Teile des Rotorschafts (24), die den feststehenden Blättern entsprechen, kleiner als die Durchmesser derjenigen Teile des Rotorschafts sind, die den angebrachten beweglichen Blättern entsprechen; wobei in Axialrichtung des Rotorschafts die jeweilige Weite derjenigen Rotorschaftsteile, die den feststehenden Blättern entsprechen, bei mindestens zwei der Stufen auf einer stromaufwärts-Seite des Dampfstroms größer als auf dessen stromabwärts-Seite ist und die Weite zwischen der letzten Stufe der beweglichen Blätter und der der letzten Stufe direkt vorhergehenden Stufe 0,6 - 0,8 mal so groß wie die Weite zwischen der ersten Stufe und der zweiten Stufe der beweglichen Blätter ist; und wobei in Axialrichtung des Rotorschafts die jeweilige Weite der Rotorschansteile, die den angebrachten beweglichen Blättern entsprechen, bei mindestens zwei der Stufen auf der stromabwärts-Seite des Dampfstroms schrittweise größer als auf dessen stromaufwärts-Seite ist und die axiale Weite der letzten Stufe der beweglichen Blätter des Abschnitts zur Anbringung der beweglichen Blätter 0,8 - 2 mal so groß wie die axiale Weite der ersten Stufe der beweglichen Blätter des Abschnitts zur Anbringung der beweglichen Blätter ist.
  16. Dampfturbinen-Kraftwerk mit einer Hochdruck-Turbine (52), einer Mitteldruck-Turbine (53) und einer Niederdruck-Turbine (54, 55), wobei Dampfeinlässe (28, 29) für jeweils die Hochdruck- und die Mitteldruck-Turbine (52, 53), die jeweils in der Hochdruck- und der Mitteldruck-Turbine (52, 53) zu beweglichen Blättern (16, 17) einer ersten Stufe führen, eine Temperatur von 610 - 660°C aufweisen und der Dampfeinlaß der Niederdruck-Turbine (54, 55), der zu beweglichen Blättern (41) einer ersten Stufe in der Niederdruck-Turbine führt, eine Temperatur von 380 - 475°C aufweist, dadurch gekennzeichnet, daß die Hochdruck-Turbine (52) in einem der Ansprüche 1 bis 6, 8 bis 10 oder 14 und die Mitteldruck-Turbine (53) in einem der Ansprüche 1 bis 5, 7, 11 bis 13 oder 15 definiert ist.
  17. Dampfturbinen-Kraftwerk nach Anspruch 16, wobei die beweglichen Blätter (16) der ersten Stufe der Hochdruck-Turbine (52) und derjenige Teil eines Rotorschafts (23) der Hochdruck-Turbine, auf dem die beweglichen Blätter der ersten Stufe angebracht sind, bei Metalltemperaturen gehalten sind, die sich nicht mehr als 40 °C unter einer Temperatur des Dampfeinlasses der Hochdruck-Turbine befinden, der zu den beweglichen Blättern der ersten Stufe führt; und wobei die beweglichen Blätter (17) der ersten Stufe der Mitteldruck-Turbine (53) und der Teil eines Rotorschafts (24) der Mitteldruck-Turbine, auf dem die beweglichen Blätter der ersten Stufe angebracht sind, bei einer Metalltemperatur gehalten sind, die sich nicht mehr als 75 °C unter einer Temperatur des Dampfeinlasses der Mitteldruck-Turbine, der zu den beweglichen Blättern der ersten Stufe führt, befindet.
  18. Kohlebefeuertes Dampfturbinen-Kraftwerk mit einem kohlegefeuerten Kessel (51), Dampfturbinen (52, 53, 54, 55), die von von dem Kessel (51) erzeugtem Dampf angetrieben werden, und einem oder zwei Generatoren (68) die von von den Dampfturbinen angetrieben werden und eine Ausgabe von mindestens 1000 MW erzeugen, dadurch gekennzeichnet, daß die Dampfturbinen eine Hochdruck-Turbine (52) nach einem der Ansprüche 1 bis 6, 8 bis 10 oder 14, eine Mitteldruck-Turbine (53) nach einem der Ansprüche 1 bis 5, 7, 11 bis 13 oder 15, wobei die Mitteldruck-Turbine (53) mit der Hochdruck-Turbine (52) verbunden ist, und zwei Niederdruck-Turbinen (54, 55) enthält, wobei sich der jeweilige Dampfeinlaß (28, 29) der Hochdruck- und der Mitteldruck-Turbine (52, 53), der zu beweglichen Blättern (16, 17) einer ersten Stufe führt, auf einer Temperatur von 610 bis 660 °C befindet und sich der Dampfeinlaß der Niederdruck-Turbine (54, 55), der zu beweglichen Blättern (41) einer ersten Stufe führt, auf einer Temperatur von 380 - 450: °C befindet und die erste Stufe der beweglichen Blätter (16, 17) der Hochdruck-Turbine (52) und/oder der Mitteldruck-Turbine (53) nach Anspruch 3 oder 4 definiert ist.
  19. Kohlebefeuertes Dampfturbinen-Kraftwerk nach Anspruch 18, wobei der von einem Überhitzer (66) des Kessels (51) auf eine um mindestens 3 °C höhere Temperatur als die Temperatur des Dampfeinlasses (28) der Hochdruck-Turbine (52) erhitzte Dampf in die beweglichen Blätter (16) der ersten Stufe der Hochdruck-Turbine (52) strömen gelassen wird, wobei der die Hochdruck-Turbine (52) verlassende Dampf von einem Wiedererhitzer (66) des Kessels (51) auf eine um mindestens 2 °C höhere Temperatur als die Temperatur des Dampfeinlasses (29) der Mitteldruck-Turbine (53), der zu deren beweglichen Blättern (17) der ersten Stufe führt, erhitzt wird, woraufhin bewirkt wird, daß der erhitzte Dampf in die beweglichen Blätter der ersten Stufe der Mitteldruck-Turbine strömt, und wobei der die Mitteldruck-Turbine verlassende Dampf von einem Abgasvorwärmer (64) des Kessels (51) auf eine um mindestens 3 °C höhere Temperatur als die Temperatur des Dampfeinlasses der Niederdruck-Turbine (54, 55) erhitzt wird, der zu deren beweglichen Blättern der ersten Stufe führt, woraufhin der erhitzte Dampf in die beweglichen Blätter der ersten Stufe der Niederdruck-Turbine strömen gelassen wird.
  20. Kraftwerk nach einem der Ansprüche 16 bis 19, wobei die Niederdruck-Dampfturbine (54, 55) einen Rotorschaft (44), auf dem Rotorschaft angebrachte bewegliche Blätter (41), feststehende Blätter (42), die einen Dampf-Zustrom auf die beweglichen Blätter (41) leiten, und ein die feststehenden Blätter (42) haltendes Innengehäuse aufweist; wobei die beweglichen Blätter (41) einen Doppelstrom-Aufbau aufweisen, bei dem auf jeder Seite in Längsrichtung des Rotorschafts, in wechselweise symmetrische Anordnung auf beiden Seiten, mindestens 8 Stufen enthalten sind, wobei die ersten Stufen der Anordnung in Längsrichtung auf einem Mittelteil des Rotorschafts angebracht sind; wobei der Rotorschaft zwischen der jeweiligen Mitte von Lagern, in denen er wellengelagert ist, einen Abstand (L) von mindestens 7000 mm und einen Minimaldurchmesser (D) an seinen den feststehenden Blätter entsprechenden Teilen von mindestens 1150 mm aufweist, wobei ein Verhältnis (L/D) zwischen dem Abstand (L) und dem Durchmesser (D) 5,4 - 6,3 beträgt und wobei er aus niederlegiertem Ni-Cr-Mo-V-Stahl mit 1 bis 2,5 Gew. % Cr und 3,0 bis 4,5 Gew. % Ni hergestellt ist; und wobei die beweglichen Blätter der letzten Stufe der Anordnung jeweils eine Länge von mindestens 1016 mm (40 Zoll) aufweisen und aus einer Legierung auf Ti-Basis hergestellt sind.
  21. Kraftwerk nach einem der Ansprüche 16 bis 20, wobei die Niederdruck-Dampfturbine (54, 55) einen Rotorschaft (44), auf dem Rotorschaft angebrachte bewegliche Blätter (41), feststehende Blätter, (42), die einen Dampf-Zustrom zu den beweglichen Blättern leiten, und ein die feststehenden Blätter haltendes Innengehäuse aufweist; wobei sich der Dampfeinlaß der Niederdruck-Turbine, der zu einem erststufigen der beweglichen Blätter führt, auf einer Temperatur von 380 - 450 °C befindet; und wobei der Rotorschaft aus niederlegiertem Stahl hergestellt ist, der 0,2 - 0,3 % C, maximal 0,05 % Si, maximal 0,1 % Mn, 3,0 bis 4,5 % Ni, 1,25 - 2.25 % Cr, 0,07 - 0,20 % Mo, 0,07 - 0,2 % V und mindestens 92,5 % Fe enthält, wobei die Prozentangaben auf das Gewicht bezogen sind.
  22. Kraftwerk nach einem der Ansprüche 16 bis 19, wobei die Niederdruck-Dampfturbine (54, 55) einen Rotorschaft (44), auf dem Rotorschaft angebrachte bewegliche Blätter (41), feststehende Blätter (42), die einen Dampf-Zustrom zu den beweglichen Blättern leiten, und ein die feststehenden Blätter haltendes Innengehäuse aufweist; wobei die beweglichen Blätter einen Doppelstrom-Aufbau aufweisen, bei dem auf jeder von zwei Seiten in Längsrichtung des Rotorschafts, in wechselweise symmetrischer Anordnung auf beiden Seiten, mindestens 8 Stufen enthalten sind und die jeweilige Länge der beweglichen Blätter von einer stromaufwärts-Seite des Dampfstroms zu einer stromabwärts-Seite länger wird, wobei eine erste Stufe der beweglichen Blätter nicht größer als 90 mm und eine letzte Stufe der beweglichen Blätter nicht länger als 1300 mm ist; wobei die Durchmesser derjenigen Teile des Rotorschafts, auf denen die beweglichen Blätter angebracht sind, größer als die Durchmesser derjenigen Teile des Rotorschafts sind, die den feststehenden Blättern entsprechen; und wobei in Axialrichtung des Rotorschafts die jeweilige Weite der Teile des Rotorschafts zur Anbringung der beweglichen Blätter auf der stromabwärts-Seite größer als auf der stromaufwärts-Seite ist und die Verhältnisse dieser Weiten zu den Längen der beweglichen Blätter innerhalb eines Bereichs von 0,15 - 1,0 von der stromaufwärts-Seite zur stromabwärts-Seite hinabnimmt.
  23. Kraftwerk nach einem der Ansprüche 16 bis 22, wobei die Niederdruck-Dampfturbine (54, 55) einen Rotorschaft (44), auf dem Rotorschaft angebrachte bewegliche Blätter (41), feststehende Blätter (42), die einen Dampf-Zustrom zu den beweglichen Blättern leiten, und ein die feststehenden Blätter haltendes Innengehäuse aufweist; wobei die beweglichen Blätter einen Doppelstrom-Aufbau aufweisen, der auf jeder von zwei Seiten in Längsrichtung des Rotorschafts, in wechselweise symmetrischer Anordnung auf beiden Seiten, mindestens 8 Stufen enthält, wobei die Längen der beweglichen Blätter von einer stromaufwärts-Seite des Dampfstroms zu einer stromabwärts-Seite länger werden, wobei eine erste Stufe der beweglichen Blätter nicht kürzer als 90 mm und eine letzte Stufe der beweglichen Blätter nicht länger als 1300 mm ist; und wobei die Längen der beweglichen Blätter entsprechenderweise benachbarter Stufen auf der stromabwärts-Seite größer als auf der stromaufwärts-Seite sind und ihre Verhältnisse zur stromabwärts-Seite hin innerhalb eines Bereichs von 1,2 - 1,7 stetig zunehmen.
  24. Kraftwerk nach einem der Ansprüche 16 bis 23, wobei die Niederdruck-Dampfturbine (54, 55) einen Rotorschaft (45), auf dem Rotorschaft angebrachte bewegliche Blätter (41), feststehende Blätter (42), die einen Dampf-Zustrom zu den beweglichen Blättern leiten, und ein die feststehenden Blätter haltendes Innengehäuse aufweist; wobei die beweglichen Blätter einen Doppelstrom-Aufbau aufweisen, der auf jeder von zwei Seiten in Längsrichtung des Rotorschafts, in wechselweise symmetrische Anordnung auf beiden Seiten, mindestens 8 Stufen beinhaltet, wobei die Längen der beweglichen Blätter von einer stromaufwärts-Seite des Dampfstroms zu einer stromabwärts-Seite länger werden, wobei eine erste Stufe der beweglichen Blätter nicht kürzer als 90 mm und eine letzte Stufe der beweglichen Blätter nicht länger als 1300 mm ist; und wobei die Durchmesser derjenigen Teile des Rotorschafts, die den feststehenden Blättern entsprechen, kleiner als die Durchmesser des Abschnitts des Rotorschafts zur Anbringung der beweglichen Blätter sind und die jeweilige in Axialrichtung des Rotorschafts genommene Weite derjenigen Teile des Rotorschafts, die den feststehenden Blättern entsprechen, auf der stromabwärts-Seite größer als auf der stromaufwärts-Seite ist und die Verhältnisse dieser Weiten zu den Längen entsprechenderweise benachbarter beweglicher Blätter entsprechender Abschnitte auf der stromabwärts-Seite schrittweise innerhalb eines Bereichs von 0,2 - 1,4 zur stromabwärts-Seite abnehmen.
  25. Kraftwerk nach einem der Ansprüche 16 bis 24, wobei die Niederdruck-Dampfturbine (54, 55) einen Rotorschaft (44), auf dem Rotorschaft angebrachte bewegliche Blätter (41), feststehende Blätter (42), die einen Dampf-Zustrom zu den beweglichen Blättern leiten, und ein die feststehenden Blätter haltendes Innengehäuse aufweist; wobei die beweglichen Blätter einen Doppelstrom-Aufbau aufweisen, der auf jeder von zwei Seiten in Axialrichtung des Rotorschafts, in wechselweise symmetrische Anordnung auf beiden Seiten, mindestens 8 Stufen beinhaltet; wobei die Durchmesser derjenigen Teile des Rotorschafts, die den feststehenden Blättern entsprechen, kleiner als die Durchmesser derjenigen Teile des Rotorschafts sind, die den angebrachten beweglichen Blättern entsprechen; wobei die jeweilige Weite in Axialrichtung des Rotorschafts derjenigen Teile des Rotorschafts, die den feststehenden Blättern entsprechen, bei mindestens drei der Stufen auf einer stromaufwärts-Seite des Dampfstroms schrittweise größer als auf dessen stromabwärts-Seite ist und die Weite zwischen der letzten Stufe der beweglichen Blätter und der der letzten Stufe direkt vorausgehenden Stufe 1,5 - 2,5 mal so groß wie die Weite zwischen der ersten Stufe und der zweiten Stufe der beweglichen Blätter ist; und wobei die jeweilige Weite der Rotorschaftsteile, die den angebrachten beweglichen Blättern entsprechen, bei mindestens drei der Stufen in Axialrichtung des Rotorschafts auf der stromabwärts-Seite des Dampfstroms schrittweise größer als auf dessen stromaufwärts-Seite ist und die Axialweite der letzten Stufe der beweglichen Blätter 2 bis 3 mal so groß wie die Axialweite der ersten Stufe der beweglichen Blätter ist.
  26. Dampfturbine nach einem der Ansprüche 1 bis 15 mit aufgebrachten Schweißschichten, die aus einem Metall mit besseren Lagereigenschaften als ein Muttermetall des Rotorschafts hergestellt sind und auf der Oberfläche jedes Wellenlagerabschnitts des Rotorschafts ausgebildet sind.
  27. Dampfturbine nach Anspruch 26, wobei mindestens drei aufgebrachte Schweißschichten gebildet sind.
  28. Dampfturbine nach Anspruch 27, wobei 5 bis 10 aufgebrachte Schweißschichten ausgebildet sind.
  29. Dampfturbine nach einem der Ansprüche 26 bis 28, wobei die äußerste Schicht der aufgebrachten Schweißschichten aus einem niederlegierten Stahl mit 0,5 bis 3 Gew. % Cr hergestellt ist.
  30. Dampfturbine nach Anspruch 29, wobei die äußerste Schicht der aufgebrachten Schweißschichten aus einem niederlegierten Stahl mit 0,01 bis 0,15 Gew. % C, 0,3 bis 1 Gew.Si, 0,3 bis 1,5 Gew. % Mn und 0,5 bis 3 Gew. % Cr sowie 0,1 bis 1,5 Gew. % Mo hergestellt ist.
EP19950113119 1995-08-21 1995-08-21 Dampfturbinenkraftanlage und Dampfturbine Expired - Lifetime EP0759499B2 (de)

Priority Applications (2)

Application Number Priority Date Filing Date Title
EP19950113119 EP0759499B2 (de) 1995-08-21 1995-08-21 Dampfturbinenkraftanlage und Dampfturbine
DE69525621T DE69525621T3 (de) 1995-08-21 1995-08-21 Dampfturbinenkraftanlage und Dampfturbine

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP19950113119 EP0759499B2 (de) 1995-08-21 1995-08-21 Dampfturbinenkraftanlage und Dampfturbine

Publications (3)

Publication Number Publication Date
EP0759499A1 EP0759499A1 (de) 1997-02-26
EP0759499B1 EP0759499B1 (de) 2002-02-27
EP0759499B2 true EP0759499B2 (de) 2005-12-14

Family

ID=8219542

Family Applications (1)

Application Number Title Priority Date Filing Date
EP19950113119 Expired - Lifetime EP0759499B2 (de) 1995-08-21 1995-08-21 Dampfturbinenkraftanlage und Dampfturbine

Country Status (2)

Country Link
EP (1) EP0759499B2 (de)
DE (1) DE69525621T3 (de)

Families Citing this family (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH0959747A (ja) * 1995-08-25 1997-03-04 Hitachi Ltd 高強度耐熱鋳鋼，蒸気タービンケーシング，蒸気タービン発電プラント及び蒸気タービン
FR2823226B1 (fr) * 2001-04-04 2004-02-20 V & M France Acier et tube en acier pour usage a haute temperature
EP1559872A1 (de) * 2004-01-30 2005-08-03 Siemens Aktiengesellschaft Strömungsmaschine
JP4664857B2 (ja) * 2006-04-28 2011-04-06 株式会社東芝 蒸気タービン
US9297277B2 (en) 2011-09-30 2016-03-29 General Electric Company Power plant
US9039365B2 (en) * 2012-01-06 2015-05-26 General Electric Company Rotor, a steam turbine and a method for producing a rotor
US20130323075A1 (en) * 2012-06-04 2013-12-05 General Electric Company Nickel-chromium-molybdenum-vanadium alloy and turbine component
US20130323522A1 (en) * 2012-06-05 2013-12-05 General Electric Company Cast superalloy pressure containment vessel
CN109356663A (zh) * 2018-12-10 2019-02-19 上海发电设备成套设计研究院有限责任公司 一种640℃~650℃汽轮机内部冷却的高温转子

Family Cites Families (16)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE383253C (de) * 1921-08-12 1923-10-11 Karl Roeder Dr Ing Doppelflussturbine fuer Daempfe und Gase
DE407717C (de) * 1921-11-22 1925-01-02 Melms & Pfenninger Komm Ges Dampfturbine der Zweiflussbauart
US3880549A (en) * 1973-11-19 1975-04-29 Stork Koninklijke Maschf Turbine
JPS57165603A (en) * 1981-04-03 1982-10-12 Hitachi Ltd Rotor shaft for steam turbine
JPS59229005A (ja) * 1983-06-10 1984-12-22 Hitachi Ltd 石炭ガス化複合発電プラント
JPH0672286B2 (ja) 1984-07-10 1994-09-14 株式会社日立製作所 ▲高▼温強度に優れたオーステナイト系ステンレス鋼
JPS62180044A (ja) 1986-02-05 1987-08-07 Hitachi Ltd 蒸気タ−ビン用ロ−タシヤフト
JPS63171856A (ja) * 1987-01-09 1988-07-15 Hitachi Ltd 耐熱鋼
EP0761836B1 (de) * 1989-02-03 2003-10-01 Hitachi, Ltd. Hitzebeständiger Stahl- und Turbinenrotor
JPH0830251B2 (ja) 1989-02-23 1996-03-27 日立金属株式会社 高温強度の優れたフェライト系耐熱鋼
JP2947913B2 (ja) 1990-10-12 1999-09-13 株式会社日立製作所 高温蒸気タービン用ロータシャフト及びその製造法
JP2631250B2 (ja) 1991-06-18 1997-07-16 新日本製鐵株式会社 ボイラ用鋼管用高強度フェライト系耐熱鋼
DE59203883D1 (de) * 1991-07-17 1995-11-09 Siemens Ag Verfahren zum Betreiben einer Gas- und Dampfturbinenanlage und Anlage zur Durchführung des Verfahrens.
SE502492C2 (sv) * 1991-12-23 1995-10-30 Abb Carbon Ab Pannanläggning med gemensamt ångsystem
JPH0734202A (ja) * 1993-07-23 1995-02-03 Toshiba Corp 蒸気タービン用ロータ
JP3315800B2 (ja) * 1994-02-22 2002-08-19 株式会社日立製作所 蒸気タービン発電プラント及び蒸気タービン

Also Published As

Publication number Publication date
DE69525621T3 (de) 2006-08-24
EP0759499B1 (de) 2002-02-27
EP0759499A1 (de) 1997-02-26
DE69525621D1 (de) 2002-04-04
DE69525621T2 (de) 2002-10-17

Similar Documents

Publication Publication Date Title
US5749228A (en) Steam-turbine power plant and steam turbine
KR100414474B1 (ko) 고강도내열주강,증기터빈케이싱,증기터빈발전플랜트및증기터빈
US6575700B2 (en) Steam turbine blade, and steam turbine and steam turbine power plant using the same
US6129514A (en) Steam turbine power-generation plant and steam turbine
EP0237170B1 (de) Hitzebeständiger Stahl und daraus hergestellte Gasturbinenteile
US20110126540A1 (en) High-strength heat resisting cast steel, method of producing the steel, and applications of the steel
EP1770184B1 (de) Martensitischer Hochfester Hitzebeständiger Gussstahl und dessen Herstellungsverfahren
US6358004B1 (en) Steam turbine power-generation plant and steam turbine
EP0759499B2 (de) Dampfturbinenkraftanlage und Dampfturbine
JP3362369B2 (ja) 蒸気タービン発電プラント及び蒸気タービン
JPH09287402A (ja) 蒸気タービン用ロータシャフト及び蒸気タービン発電プラントとその蒸気タービン
JP3716684B2 (ja) 高強度マルテンサイト鋼
JP3661456B2 (ja) 低圧蒸気タービンの最終段動翼
JPH10317105A (ja) 高強度鋼，蒸気タービン長翼及び蒸気タービン
JP3632272B2 (ja) 蒸気タービン用ロータシャフトとその製造法及び蒸気タービン発電プラントとその蒸気タービン
JP3800630B2 (ja) 蒸気タービン発電プラント及び低圧蒸気タービンの最終段動翼とその製造法
US6305078B1 (en) Method of making a turbine blade
JP3362371B2 (ja) 蒸気タービン及び蒸気タービン発電プラント
JPWO1997030272A1 (ja) 蒸気タービン発電プラント及び蒸気タービン
JPH1193603A (ja) 蒸気タービン発電プラント及び蒸気タービン
JP2004150443A (ja) 蒸気タービン翼とそれを用いた蒸気タービン及び蒸気タービン発電プラント

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

AK Designated contracting states

Kind code of ref document: A1

Designated state(s): CH DE FR GB IT LI

17P Request for examination filed

Effective date: 19970822

17Q First examination report despatched

Effective date: 19990120

GRAG Despatch of communication of intention to grant

Free format text: ORIGINAL CODE: EPIDOS AGRA

GRAG Despatch of communication of intention to grant

Free format text: ORIGINAL CODE: EPIDOS AGRA

APAB Appeal dossier modified

Free format text: ORIGINAL CODE: EPIDOS NOAPE

APAB Appeal dossier modified

Free format text: ORIGINAL CODE: EPIDOS NOAPE

APBJ Interlocutory revision of appeal recorded

Free format text: ORIGINAL CODE: EPIDOS IRAPE

GRAG Despatch of communication of intention to grant

Free format text: ORIGINAL CODE: EPIDOS AGRA

GRAH Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOS IGRA

GRAH Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOS IGRA

REG Reference to a national code

Ref country code: GB

Ref legal event code: IF02

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

AK Designated contracting states

Kind code of ref document: B1

Designated state(s): CH DE FR GB IT LI

REG Reference to a national code

Ref country code: CH

Ref legal event code: EP

REG Reference to a national code

Ref country code: CH

Ref legal event code: NV

Representative=s name: ISLER & PEDRAZZINI AG

REF Corresponds to:

Ref document number: 69525621

Country of ref document: DE

Date of ref document: 20020404

ET Fr: translation filed
REG Reference to a national code

Ref country code: CH

Ref legal event code: PK

Free format text: BERICHTIGUNGEN

Ref country code: CH

Ref legal event code: NV

Representative=s name: TROESCH SCHEIDEGGER WERNER AG

PLBQ Unpublished change to opponent data

Free format text: ORIGINAL CODE: EPIDOS OPPO

PLBI Opposition filed

Free format text: ORIGINAL CODE: 0009260

PLBF Reply of patent proprietor to notice(s) of opposition

Free format text: ORIGINAL CODE: EPIDOS OBSO

26 Opposition filed

Opponent name: ALSTOM (SWITZERLAND) LTD

Effective date: 20021125

PLBF Reply of patent proprietor to notice(s) of opposition

Free format text: ORIGINAL CODE: EPIDOS OBSO

PUAH Patent maintained in amended form

Free format text: ORIGINAL CODE: 0009272

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: PATENT MAINTAINED AS AMENDED

27A Patent maintained in amended form

Effective date: 20051214

AK Designated contracting states

Kind code of ref document: B2

Designated state(s): CH DE FR GB IT LI

REG Reference to a national code

Ref country code: CH

Ref legal event code: AEN

Free format text: AUFRECHTERHALTUNG DES PATENTES IN GEAENDERTER FORM

ET3 Fr: translation filed ** decision concerning opposition
PLAB Opposition data, opponent's data or that of the opponent's representative modified

Free format text: ORIGINAL CODE: 0009299OPPO

REG Reference to a national code

Ref country code: DE

Ref legal event code: R082

Ref document number: 69525621

Country of ref document: DE

Representative=s name: PATENTANWAELTE STREHL, SCHUEBEL-HOPF & PARTNER, DE

REG Reference to a national code

Ref country code: DE

Ref legal event code: R082

Ref document number: 69525621

Country of ref document: DE

Representative=s name: STREHL SCHUEBEL-HOPF & PARTNER MBB PATENTANWAE, DE

Effective date: 20140730

Ref country code: DE

Ref legal event code: R082

Ref document number: 69525621

Country of ref document: DE

Representative=s name: PATENTANWAELTE STREHL, SCHUEBEL-HOPF & PARTNER, DE

Effective date: 20140730

Ref country code: DE

Ref legal event code: R081

Ref document number: 69525621

Country of ref document: DE

Owner name: MITSUBISHI HITACHI POWER SYSTEMS, LTD., YOKOHA, JP

Free format text: FORMER OWNER: HITACHI, LTD., TOKYO, JP

Effective date: 20140730

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: DE

Payment date: 20140813

Year of fee payment: 20

Ref country code: CH

Payment date: 20140812

Year of fee payment: 20

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: FR

Payment date: 20140808

Year of fee payment: 20

Ref country code: GB

Payment date: 20140820

Year of fee payment: 20

REG Reference to a national code

Ref country code: FR

Ref legal event code: TP

Owner name: MITSUBISHI HITACHI POWER SYSTEMS, LTD., JP

Effective date: 20141124

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: IT

Payment date: 20140819

Year of fee payment: 20

REG Reference to a national code

Ref country code: CH

Ref legal event code: PFUS

Owner name: MITSUBISHI HITACHI POWER SYSTEMS, LTD., JP

Free format text: FORMER OWNER: HITACHI, LTD., JP

Ref country code: CH

Ref legal event code: PCOW

Free format text: NEW ADDRESS: 6-6, MARUNOUCHI 1-CHOME, CHIYODA-KU, TOKYO 100-8280 (JP)

REG Reference to a national code

Ref country code: GB

Ref legal event code: 732E

Free format text: REGISTERED BETWEEN 20150528 AND 20150603

REG Reference to a national code

Ref country code: DE

Ref legal event code: R071

Ref document number: 69525621

Country of ref document: DE

REG Reference to a national code

Ref country code: CH

Ref legal event code: PL

REG Reference to a national code

Ref country code: GB

Ref legal event code: PE20

Expiry date: 20150820

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: GB

Free format text: LAPSE BECAUSE OF EXPIRATION OF PROTECTION

Effective date: 20150820