CN113982701B - Novel 1000 MW-level secondary reheating 630 ℃ steam turbine and matched double-engine regenerative system - Google Patents
Novel 1000 MW-level secondary reheating 630 ℃ steam turbine and matched double-engine regenerative system Download PDFInfo
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- CN113982701B CN113982701B CN202111116840.0A CN202111116840A CN113982701B CN 113982701 B CN113982701 B CN 113982701B CN 202111116840 A CN202111116840 A CN 202111116840A CN 113982701 B CN113982701 B CN 113982701B
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- 230000001172 regenerating effect Effects 0.000 title claims abstract description 47
- 238000003303 reheating Methods 0.000 title claims abstract description 16
- 238000011084 recovery Methods 0.000 claims abstract description 22
- 238000000605 extraction Methods 0.000 claims description 51
- 230000001105 regulatory effect Effects 0.000 claims description 20
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 claims description 19
- 244000161999 Acacia greggii Species 0.000 claims description 11
- 235000004608 catclaw acacia Nutrition 0.000 claims description 11
- 238000005192 partition Methods 0.000 claims description 6
- 230000001502 supplementing effect Effects 0.000 claims description 5
- 210000004907 gland Anatomy 0.000 claims description 4
- 230000008901 benefit Effects 0.000 abstract description 4
- 230000006872 improvement Effects 0.000 abstract description 4
- 230000003090 exacerbative effect Effects 0.000 abstract description 3
- 238000004519 manufacturing process Methods 0.000 abstract description 3
- 230000007547 defect Effects 0.000 abstract description 2
- 238000013461 design Methods 0.000 description 12
- 230000008859 change Effects 0.000 description 6
- 238000006243 chemical reaction Methods 0.000 description 6
- 238000003466 welding Methods 0.000 description 6
- 238000011161 development Methods 0.000 description 4
- 230000018109 developmental process Effects 0.000 description 4
- 239000000463 material Substances 0.000 description 4
- 229910001018 Cast iron Inorganic materials 0.000 description 2
- 230000006978 adaptation Effects 0.000 description 2
- 238000005516 engineering process Methods 0.000 description 2
- 230000007774 longterm Effects 0.000 description 2
- 230000007246 mechanism Effects 0.000 description 2
- 238000005457 optimization Methods 0.000 description 2
- 238000010248 power generation Methods 0.000 description 2
- 238000007789 sealing Methods 0.000 description 2
- 230000008646 thermal stress Effects 0.000 description 2
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- 230000002441 reversible effect Effects 0.000 description 1
- 230000003068 static effect Effects 0.000 description 1
- 230000035882 stress Effects 0.000 description 1
Classifications
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- 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
- F01D13/00—Combinations of two or more machines or engines
- F01D13/02—Working-fluid interconnection of machines or engines
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01D—NON-POSITIVE DISPLACEMENT MACHINES OR ENGINES, e.g. STEAM TURBINES
- F01D25/00—Component parts, details, or accessories, not provided for in, or of interest apart from, other groups
- F01D25/16—Arrangement of bearings; Supporting or mounting bearings in casings
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01K—STEAM ENGINE PLANTS; STEAM ACCUMULATORS; ENGINE PLANTS NOT OTHERWISE PROVIDED FOR; ENGINES USING SPECIAL WORKING FLUIDS OR CYCLES
- F01K7/00—Steam engine plants characterised by the use of specific types of engine; Plants or engines characterised by their use of special steam systems, cycles or processes; Control means specially adapted for such systems, cycles or processes; Use of withdrawn or exhaust steam for feed-water heating
- F01K7/34—Steam engine plants characterised by the use of specific types of engine; Plants or engines characterised by their use of special steam systems, cycles or processes; Control means specially adapted for such systems, cycles or processes; Use of withdrawn or exhaust steam for feed-water heating the engines being of extraction or non-condensing type; Use of steam for feed-water heating
- F01K7/345—Control or safety-means particular thereto
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01K—STEAM ENGINE PLANTS; STEAM ACCUMULATORS; ENGINE PLANTS NOT OTHERWISE PROVIDED FOR; ENGINES USING SPECIAL WORKING FLUIDS OR CYCLES
- F01K7/00—Steam engine plants characterised by the use of specific types of engine; Plants or engines characterised by their use of special steam systems, cycles or processes; Control means specially adapted for such systems, cycles or processes; Use of withdrawn or exhaust steam for feed-water heating
- F01K7/34—Steam engine plants characterised by the use of specific types of engine; Plants or engines characterised by their use of special steam systems, cycles or processes; Control means specially adapted for such systems, cycles or processes; Use of withdrawn or exhaust steam for feed-water heating the engines being of extraction or non-condensing type; Use of steam for feed-water heating
- F01K7/38—Steam engine plants characterised by the use of specific types of engine; Plants or engines characterised by their use of special steam systems, cycles or processes; Control means specially adapted for such systems, cycles or processes; Use of withdrawn or exhaust steam for feed-water heating the engines being of extraction or non-condensing type; Use of steam for feed-water heating the engines being of turbine type
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01K—STEAM ENGINE PLANTS; STEAM ACCUMULATORS; ENGINE PLANTS NOT OTHERWISE PROVIDED FOR; ENGINES USING SPECIAL WORKING FLUIDS OR CYCLES
- F01K7/00—Steam engine plants characterised by the use of specific types of engine; Plants or engines characterised by their use of special steam systems, cycles or processes; Control means specially adapted for such systems, cycles or processes; Use of withdrawn or exhaust steam for feed-water heating
- F01K7/34—Steam engine plants characterised by the use of specific types of engine; Plants or engines characterised by their use of special steam systems, cycles or processes; Control means specially adapted for such systems, cycles or processes; Use of withdrawn or exhaust steam for feed-water heating the engines being of extraction or non-condensing type; Use of steam for feed-water heating
- F01K7/40—Use of two or more feed-water heaters in series
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Abstract
Novel 1000MW grade secondary reheat 630 ℃ steam turbine and supporting double machine regenerative system. In particular to a steam turbine and a double-engine regenerative system. The invention aims to overcome the defect that the existing double-reheat steam turbine has a regenerative systemThe loss increases, thereby influencing the turbine performance benefit brought by the steam parameter improvement, greatly improving the manufacturing cost and exacerbating the problem of high-temperature application risk of the high-pressure heater. A novel 1000MW grade secondary reheating 630 ℃ steam turbine and a matched double-machine regenerative system comprise a double-machine regenerative system and a steam turbine; the steam turbine is matched with a double-machine regenerative system; the double-machine heat recovery system is connected with the ultrahigh-pressure module, the medium-pressure module, the first low-pressure module and the second low-pressure module through pipelines respectively, and the connection mode of the first low-pressure module and the second low-pressure module is the same as that of the double-machine heat recovery system. The invention can be used for the 1000 MW-grade 630 ℃ steam parameter double reheat thermal power project.
Description
Technical Field
The invention relates to the technical field of steam turbines and double-machine heat recovery systems, in particular to a novel 1000 MW-level secondary heat recovery 630 ℃ steam turbine and a matched double-machine heat recovery system.
Background
The main steam temperature curing parameter of the existing secondary reheat steam turbine is 600-605 ℃, the reheat temperature curing parameter is 620-622 ℃, the development of intermediate-stage parameter grade steam turbine design and system innovation application research demonstration are urgently needed in the technical development of the ultra-high steam parameter application field, the breakthrough of the power generation efficiency of a power station is realized, and the national coal-electricity clean high-efficiency sustainable energy development layout is created; in addition, the conventional parameter secondary reheat steam turbine is designed as a conventional regenerative system, the steam extraction of the intermediate stage of the through flow can influence the flow efficiency of steam in the through flow, and the high pressure steam superheat degree and the medium pressure steam extraction of the 630 ℃ steam inlet temperature exist, so that the regenerative systemThe loss increases, thereby influences steam turbine performance income that steam parameter promoted and brings, and boiler main reheat steam pipe, backheating steam extraction pipeline and high pressure heater are promoted by a wide margin because of temperature promotion cost simultaneously to aggravate high temperature application risk of high pressure heater, need carry out corresponding backheating system innovation design urgently.
In summary, the existing double reheat turbine has a regenerative systemThe loss increases, thereby influencing the turbine performance benefit brought by the steam parameter improvement, greatly improving the manufacturing cost and exacerbating the problem of high-temperature application risk of the high-pressure heater.
Disclosure of Invention
The invention aims to overcome the defect that the existing double-reheat steam turbine has a regenerative systemThe loss increases, thereby influencing the turbine performance benefit caused by the steam parameter increase, greatly increasing the manufacturing cost and exacerbating the problem of high-temperature application risk of the high-pressure heater. And further provides a novel 1000 MW-level double-reheat 630 ℃ steam turbine and a matched double-machine regenerative system.
The technical scheme of the invention is as follows:
A novel 1000MW grade secondary reheating 630 ℃ steam turbine and a matched double-machine regenerative system comprise a steam turbine and a double-machine regenerative system;
the steam turbine is matched with a double-machine regenerative system;
The steam turbine comprises an ultrahigh pressure module, a high pressure module, a medium pressure module, a first low pressure module, a second low pressure module, a first bearing box, a second bearing box, a third bearing box, a fourth bearing box, a fifth bearing box, a sixth bearing box, a plurality of centering beams and a plurality of lower cylinder cat claws;
The electric end of the ultrahigh pressure module is fixedly connected with one end of a second bearing box through the centering beam, the other end of the second bearing box is fixedly connected with the electric end of the high pressure module through the centering beam, the electric end of the high pressure module is in sliding contact with one end of a third bearing box through a lower cylinder cat claw, the other end of the third bearing box is in sliding contact with the electric end of the middle pressure module through a lower cylinder cat claw, the electric end of the middle pressure module is fixedly connected with one end of a fourth bearing box through the centering beam, the other end of the fourth bearing box is fixedly connected with the electric end of a first low pressure module, the electric end of the first low pressure module is fixedly connected with one end of a fifth bearing box, the other end of the fifth bearing box is fixedly connected with the electric end of the second low pressure module, the electric end of the second low pressure module is fixedly connected with one end of a sixth bearing box, and the other end of the sixth bearing box is fixedly connected with a generator;
The double-machine heat recovery system is connected with the ultrahigh-pressure module, the medium-pressure module, the first low-pressure module and the second low-pressure module through pipelines respectively, and the connection mode of the first low-pressure module and the second low-pressure module is the same as that of the double-machine heat recovery system.
Novel 1000 MW-level secondary reheating 630 ℃ steam turbine and matched double steam turbine compared with the prior art, the mechanical regenerative system has the following effects:
According to the novel 1000MW grade secondary reheating 630 ℃ steam turbine and the matched double-machine regenerative system, the ultra-high pressure module, the medium pressure module, the first low pressure module, the second low pressure module, the first bearing box, the second bearing box, the third bearing box, the fourth bearing box, the fifth bearing box, the sixth bearing box and the generator form the whole machine, the whole machine is suitable for the design of steam inlet parameters at 35MPa/615 ℃/630 ℃/630 ℃, the design heat consumption of the whole machine is reduced by the primary parameters of the steam turbine, the circulation heat efficiency is obviously improved, the reliability, the safety and the stability of long-term application of the 630 ℃ steam parameters are guaranteed, meanwhile, the steam flow efficiency and the circulation efficiency of the steam regenerative system (optimizing the regenerative series, reducing the regenerative extraction quality) in the high pressure module and the medium pressure module of the steam turbine can be further improved, the cost and the high temperature risk of a reheat steam pipeline of the boiler are reduced, and meanwhile, the main circulation steam turbine drives a water feeding pump to operate, and the operation efficiency is higher than that of a conventional pump steam turbine. The invention design and application of the main steam turbine and the regenerative system can promote the development and breakthrough of the power generation technology of 650 ℃ and 700 ℃ steam parameter engineering steam turbine material selection, body structure design, thermodynamic system innovation application and the like. The invention aims to solve the problems that the double reheat steam turbines in the prior art are all designed as conventional regenerative systems, the steam extraction of the intermediate stage of the through flow can influence the flow efficiency of steam in the through flow, and the high pressure steam extraction and the medium pressure steam extraction at the steam inlet temperature of 630 ℃ have larger steam superheat degree, and the regenerative systems The loss increases, thereby influencing the steam turbine performance benefit brought by the steam parameter improvement, and the boiler main reheat steam pipeline, the regenerative steam extraction pipeline and the high-pressure heater are also greatly improved due to the temperature improvement cost, and the problem of high-temperature application risk of the high-pressure heater is aggravated.
Drawings
FIG. 1 is a front view of a steam turbine of the present invention;
FIG. 2 is a top view of the steam turbine of the present invention;
FIG. 3 is a schematic view of a longitudinal cross-sectional structure of a steam turbine according to the present invention;
FIG. 4 is an enlarged view of a portion of FIG. 3 at A;
FIG. 5 is a partial enlarged view of FIG. 3 at B;
FIG. 6 is an enlarged view of a portion of FIG. 3 at C;
Fig. 7 is a schematic diagram of a dual-engine regenerator system and steam turbine of the present invention.
Detailed Description
The first embodiment is as follows: referring to fig. 1 to 7, a novel 1000MW grade double reheat 630 ℃ steam turbine and a matched double heat recovery system according to the present embodiment are described, and the novel 1000MW grade double reheat 630 ℃ steam turbine and the matched double heat recovery system comprise a steam turbine and a double heat recovery system 11;
The steam turbine is matched with a double-engine regenerative system 11;
The steam turbine comprises an ultrahigh pressure module 1, a high pressure module 2, a medium pressure module 3, a first low pressure module 4, a second low pressure module 5, a first bearing box 6, a second bearing box 7, a third bearing box 8, a fourth bearing box 9, a fifth bearing box 10, a sixth bearing box 11, a plurality of centering beams and a plurality of lower cylinder cat claws;
the electric end of the ultrahigh pressure module 1 is fixedly connected with one end of a first bearing box 6 through a centering beam, the electric end of the ultrahigh pressure module 1 is fixedly connected with one end of a second bearing box 7 through the centering beam, the other end of the second bearing box 7 is fixedly connected with one end of a third bearing box 8 through a lower cylinder cat claw, the other end of the third bearing box 8 is in sliding contact with one end of a middle pressure module 3 through a lower cylinder cat claw, the electric end of the middle pressure module 3 is fixedly connected with one end of a fourth bearing box 9 through the centering beam, the other end of the fourth bearing box 9 is fixedly connected with one end of a first low pressure module 4, the electric end of the first low pressure module 4 is fixedly connected with one end of a fifth bearing box 10, the other end of the fifth bearing box 10 is fixedly connected with one end of the second low pressure module 5, the electric end of the second low pressure module 5 is fixedly connected with one end of a sixth bearing box 11, and the other end of the sixth bearing box 11 is fixedly connected with a generator 12;
The double-machine heat recovery system 11 is respectively connected with the ultrahigh-pressure module 1, the medium-pressure module 3, the first low-pressure module 4 and the second low-pressure module 5 through pipelines, and the connection mode of the first low-pressure module 4 and the second low-pressure module 5 is the same as that of the double-machine heat recovery system 11.
The ultra-high pressure module 1 and the high pressure module 2 are symmetrically arranged in a single flow mode, the ultra-high pressure rotor 1-6 and the high pressure rotor 2-6 are provided with the ultra-high pressure balance drum steam seal 1-5 and the high pressure balance drum steam seal 2-5, the ultra-high pressure balance drum steam seal 1-5 and the high pressure balance drum steam seal 2-5 are designed by adopting a single-cylinder self-balancing thrust system, and the ultra-high pressure module 1 and the high pressure module 2 are symmetrically arranged in a single flow mode, so that the balance of the thrust of the whole machine under the variable working condition is more facilitated, and the middle pressure module 3, the first low pressure module 4 and the second low pressure module 5 are in double-flow distribution and the thrust is self-balanced.
The second embodiment is as follows: the description of the present embodiment is made with reference to fig. 7, in which the two-unit heat recovery system 11 of the present embodiment includes a first unit heat recovery system and a second unit heat recovery system;
The first unit regenerative system comprises a condenser 11-3, a condenser inlet pipeline 11-4, a condensate pump, a vapor seal cooler, a No. 9 low-pressure heater 11-5, a No. 9 low-pressure heater extraction pipeline 11-6, a No. 10 low-pressure heater 11-7, a No. 10 low-pressure heater extraction pipeline 11-8, a No. 11 low-pressure heater 11-9, a No. 11 low-pressure heater extraction pipeline 11-10, a No. 12 low-pressure heater 11-11 and a No. 12 low-pressure heater extraction pipeline 11-12;
The first low-pressure module 4 is connected with the No. 9 low-pressure heater 11-5 through the No. 9 low-pressure heater steam extraction pipeline 11-6, the first low-pressure module 4 is connected with the No. 10 low-pressure heater 11-7 through the No. 10 low-pressure heater steam extraction pipeline 11-8, the first low-pressure module 4 is connected with the No. 11 low-pressure heater 11-9 through the No. 11 low-pressure heater steam extraction pipeline 11-10, the first low-pressure module 4 is connected with the No. 12 low-pressure heater 11-11 through the No. 12 low-pressure heater steam extraction pipeline 11-12, the first low-pressure module 4 is connected with the condenser 11-3 through the condenser steam inlet pipeline 11-4, the No. 9 low-pressure heater 11-5, the No. 10 low-pressure heater 11-7, the No. 11 low-pressure heater 11-9, the No. 12 low-pressure heater 11-11, the steam seal cooler and the condenser 11-3 are sequentially connected from right to left along the length direction of the double-engine system 11, the No. 12 low-pressure heater 11-11, the water pump, the No. 12 condenser and the No. 11-3 are connected with the condenser 11-3 through the condenser steam seal cooler and the condenser 11-3.
The second unit regenerative system comprises a main circulation water supply pump turbine 11-1, a main circulation water supply pump turbine steam inlet pipeline 11-2, a first high-pressure heater 11-13, a first high-pressure heater steam extraction pipeline 11-14, a second high-pressure heater 11-15, a second high-pressure heater steam extraction pipeline 11-16, a third high-pressure heater 11-17, a third high-pressure heater steam extraction pipeline 11-18, a fourth high-pressure heater 11-19, a fourth high-pressure heater steam extraction pipeline 11-20, a fifth high-pressure heater 11-21, a fifth high-pressure heater steam extraction pipeline 11-22, a deaerator 11-23, a deaerator steam extraction pipeline 11-24, a seventh low-pressure heater 11-25, a main circulation water supply pump turbine steam extraction pipeline 11-26, an overflow adjusting valve 11-27, an overflow pipeline 11-28 and a eighth low-pressure heater 11-29;
The ultra-high pressure module 1 is connected with the main circulation water supply pump turbine 11-1 through the main circulation water supply pump turbine steam inlet pipeline 11-2, the ultra-high pressure module 1 is connected with the first high pressure heater 11-13 through the ultra-high pressure exhaust pipeline in the ultra-high pressure module 1, the main circulation water supply pump turbine 11-1 is respectively connected with the second high pressure heater steam extraction pipeline 11-16, the third high pressure heater steam extraction pipeline 11-18, the fourth high pressure heater steam extraction pipeline 11-20, the fifth high pressure heater steam extraction pipeline 11-22, the deaerator steam extraction pipeline 11-24, the main circulation water supply pump turbine steam exhaust pipeline 11-26 and the overflow pipeline 11-28 through the corresponding second high pressure heater 11-15, the third high pressure heater 11-17, the fourth high pressure heater 11-19, the fifth high pressure heater 11-21, the deaerator 11-23, the seventh low pressure heater 11-25 and the overflow regulating valve 11-27, the overflow adjusting valve 11-27 is connected with the eighth low-pressure heater 11-29 through the overflow pipeline 11-28, the middle-pressure module 3 is connected with the eighth low-pressure heater 11-29 through a middle-pressure exhaust pipeline in the middle-pressure module 3, the first high-pressure heater 11-13 is connected with the boiler through the first high-pressure heater steam extraction pipeline 11-14, the first high-pressure heater 11-13, the second high-pressure heater 11-15, the third high-pressure heater 11-17, the fourth high-pressure heater 11-19, the fifth high-pressure heater 11-21, the deaerator 11-23, the seventh low-pressure heater 11-25, the eighth low-pressure heater 11-29 and the 9 low-pressure heater 11-5 are sequentially connected from right to left along the length direction of the dual-machine regenerative system 11.
The other is the same as in the first embodiment.
And a third specific embodiment: the present embodiment is described with reference to fig. 1 to 3, which further includes two ultra-high pressure main steam adjusting and supplementing combined valves 13, two high pressure main steam adjusting combined valves 14, and two medium pressure main steam adjusting combined valves 15;
The two ultrahigh-pressure main steam regulating and supplementing combined valves 13 are symmetrically arranged on two sides of the ultrahigh-pressure module 1 respectively, the two high-pressure main steam regulating combined valves 14 are symmetrically arranged on two sides of the ultrahigh-pressure module 1 respectively in the high-pressure module 2, and the two medium-pressure main steam regulating combined valves 15 are symmetrically arranged on two sides of the medium-pressure module 3 respectively.
The two ultrahigh-pressure main steam regulating and supplementing combined valves 13, the two high-pressure main steam regulating combined valves 14 and the two medium-pressure main steam regulating combined valves 15 are in a structure without steam guide pipes and are rigidly and directly connected with the cylinder. Other embodiments are the same as one or the same as the embodiments.
The specific embodiment IV is as follows: the ultra-high pressure module 1 of the present embodiment includes an ultra-high pressure outer cylinder 1-1, an ultra-high pressure inner cylinder 1-2, an ultra-high pressure exhaust side end gland seal 1-3, an ultra-high pressure intake side end gland seal 1-4, an ultra-high pressure balance drum gland seal 1-5, an ultra-high pressure rotor 1-6, ultra-high pressure moving blades, and ultra-high pressure stationary blades, described with reference to fig. 1 to 3;
The inside of the ultrahigh pressure outer cylinder 1-1 is provided with an ultrahigh pressure inner cylinder 1-2, an ultrahigh pressure rotor 1-6 is arranged in the inner horizontal center of the ultrahigh pressure inner cylinder 1-2, an ultrahigh pressure steam exhaust side end steam seal 1-3 is assembled at the end adjusting end of the ultrahigh pressure outer cylinder 1-1, an ultrahigh pressure steam inlet side end steam seal 1-4 is assembled at the electric end of the ultrahigh pressure outer cylinder 1-1, an ultrahigh pressure balance drum steam seal 1-5 is assembled at the electric end of the ultrahigh pressure inner cylinder 1-2, and ultrahigh pressure moving blades and ultrahigh pressure stationary blades are respectively assembled on the ultrahigh pressure rotor 1-6 and the ultrahigh pressure inner cylinder 1-2.
The arrangement is that the ultrahigh pressure module 1 adopts a 2X 180-degree tangential volute steam inlet structure, so that the pressure loss of steam at the inlet position of the cylinder body can be effectively reduced, and the kinetic energy conversion efficiency of the steam is improved. The other features are the same as in any one of the first to third embodiments.
Fifth embodiment: referring to fig. 3, the high-pressure module 2 of the present embodiment includes a high-pressure outer cylinder 2-1, a high-pressure inner cylinder 2-2, a high-pressure exhaust side end seal 2-3, a high-pressure intake side end seal 2-4, a high-pressure balance drum seal 2-5, a high-pressure rotor 2-6, high-pressure moving blades, and high-pressure stationary blades;
The high-pressure inner cylinder 2-2 is arranged in the high-pressure outer cylinder 2-1, the high-pressure rotor 2-6 is arranged in the inner horizontal center of the high-pressure inner cylinder 2-2 and is concentric with the ultrahigh-pressure rotor 1-6, the high-pressure steam inlet side steam seal 2-4 is assembled at the adjusting end of the high-pressure outer cylinder 2-1, the high-pressure steam outlet side steam seal 2-3 is assembled at the electric end of the high-pressure outer cylinder 2-1, the high-pressure balance drum steam seal 2-5 is assembled at the adjusting end of the high-pressure outer cylinder 2-1, and the high-pressure moving blades and the high-pressure stationary blades are respectively assembled on the high-pressure rotor 2-6 and the high-pressure inner cylinder 2-2.
The arrangement is that the high-pressure module 2 adopts a 2X 180-degree tangential volute steam inlet structure, so that the pressure loss of steam at the inlet position of the cylinder body can be effectively reduced, and the kinetic energy conversion efficiency of the steam is improved. The other features are the same as in any one of the first to fourth embodiments.
Specific embodiment six: referring to fig. 3, the medium pressure module 3 of the present embodiment includes a medium pressure outer cylinder 3-1, a medium pressure inner cylinder 3-2, two medium pressure exhaust side steam seals 3-3, a medium pressure rotor 3-4, a medium pressure forward moving blade, and a medium pressure forward stationary blade;
The inside of the medium-pressure outer cylinder 3-1 is provided with a medium-pressure inner cylinder 3-2, a medium-pressure rotor 3-4 is arranged in the horizontal center of the inside of the medium-pressure inner cylinder 3-2, the medium-pressure rotor 3-4 is concentric with the ultra-high-pressure rotor 1-6 and the high-pressure rotor 2-6, one medium-pressure steam exhaust side steam seal 3-3 is arranged at the end of the medium-pressure outer cylinder 3-1, the other medium-pressure steam exhaust side steam seal 3-3 is arranged at the electric end of the medium-pressure outer cylinder 3-1, and medium-pressure positive direction moving blades and medium-pressure positive direction stationary blades are respectively assembled on the medium-pressure rotor 3-4 and the medium-pressure inner cylinder 3-2.
The medium-pressure rotor adopts a welding structure, so that the adaptability to the steam temperature of 630 ℃ and the application reliability and safety can be effectively improved. The arrangement is that the medium-pressure module 3 adopts a 2X 180-degree tangential volute steam inlet structure, so that the pressure loss of steam at the inlet position of the cylinder body can be effectively reduced, and the kinetic energy conversion efficiency of the steam is improved. The other features are the same as in any one of the first to fifth embodiments.
Seventh embodiment: the present embodiment will be described with reference to fig. 3, in which the first low-voltage module 4 and the second low-voltage module 5 have the same structure;
the first low-pressure module 4 comprises a low-pressure outer cylinder 4-1, a low-pressure inner cylinder 4-2, two low-pressure exhaust side end steam seals 4-3, two end corrugated sections 4-4, a low-pressure rotor 4-5, a low-pressure square moving blade, a low-pressure square stationary blade and a partition sleeve;
The low-pressure outer cylinder 4-1 is internally provided with a low-pressure inner cylinder 4-2, the low-pressure inner cylinder 4-2 is internally provided with a low-pressure rotor 4-5, one low-pressure exhaust side end steam seal 4-3 and one end corrugated section 4-4 are sequentially arranged at the end adjusting end of the low-pressure outer cylinder 4-1, the other end corrugated section 4-4 and one low-pressure exhaust side end steam seal 4-3 are sequentially arranged at the electric end of the low-pressure outer cylinder 4-1, and the low-pressure square moving blades and the low-pressure square stationary blades are respectively assembled on the low-pressure rotor 4-5, the low-pressure inner cylinder and the partition plate sleeve.
The first low-pressure module 4 adopts the 360-degree volute steam inlet type low-pressure integral cast iron inner cylinder, has good rigidity and small deformation, can prevent the middle-divided surface from deforming to generate steam leakage loss, can effectively reduce the pressure loss at the inlet position by the volute steam inlet, improves the efficiency of the low-pressure cylinder, and the low-pressure inner cylinder 4-2 is located at the outer cylinder supporting leg on the foundation through the supporting arm, namely the low-pressure inner cylinder 4-2 adopts a floor type structure, so that the low-pressure inner cylinder is more suitable for large-range vacuum change and steam exhaust temperature change, and can always ensure the accurate centering of a rotor and a stator part. The other features are the same as in any one of the first to sixth embodiments.
Eighth embodiment: the present embodiment will be described with reference to fig. 3, which also includes a medium-low pressure communication pipe 16,
The medium-low pressure communicating pipe 16 is arranged right above the medium-pressure module 3, the fourth bearing box 9, the first low pressure module 4, the fifth bearing box 10 and the second low pressure module 5;
the medium-low pressure communicating pipe 16 comprises a first connecting pipe 16-1, a second connecting pipe 16-2, a third connecting pipe 16-3, a fourth connecting pipe 16-4 and a straight pipe 16-5;
The first connecting pipe 16-1, the second connecting pipe 16-2, the third connecting pipe 16-3, the fourth connecting pipe 16-4 and the straight pipe 16-5 are integrated;
The first connecting pipe 16-1, the second connecting pipe 16-2, the third connecting pipe 16-3 and the fourth connecting pipe 16-4 are all arranged below the straight pipe 16-5, the first connecting pipe 16-1 is connected with the end adjusting end of the middle-pressure outer cylinder 3-1 and communicated with each other, the second connecting pipe 16-2 is connected with the electric end of the middle-pressure outer cylinder 3-1 and communicated with each other, the third connecting pipe 16-3 is connected with the middle part of the low-pressure outer cylinder 4-1 and communicated with each other, and the fourth connecting pipe 16-4 is connected with the middle part of the low-pressure outer cylinder of the second low-pressure module 5 and communicated with each other.
The other features are the same as in any one of the first to seventh embodiments.
Detailed description nine: the present embodiment is described with reference to fig. 1 to 3, the steam turbine of the present embodiment further includes a thrust bearing,
The thrust bearing is arranged on the second bearing box 7, and the absolute dead points are respectively positioned at the intersection points of the transverse positioning key and the longitudinal positioning key at the bottoms of the first low-pressure module 4, the second low-pressure module 5 and the third bearing box 8.
The setting is that bearing box 6, no. two bearing boxes 7, no. three bearing boxes 8, no. four bearing boxes 9, no. five bearing boxes 10 and No. six bearing boxes 11 all adopt the floor structure to support on the bed frame, the end and the electricity end of transferring of super high pressure outer cylinder 1-1 and high pressure outer cylinder 2-1 are respectively supported on bearing box 6, no. two bearing boxes 7 and No. three bearing boxes 8 through lower cat claw, super high pressure outer cylinder 1-1 and high pressure outer cylinder 2-1 adopt centering Liang Tuila mechanism and bearing box axial fixity, change shafting case stress position in order to reduce the effort of cylinder body to the bearing box, super high pressure cylinder, no. 1 bearing box 6 and No. two bearing boxes 7 expand to the aircraft nose direction with No. three bearing boxes 8 as absolute dead center. The regulating end and the electric end of the middle pressure outer cylinder 3-1 are respectively supported on a third bearing box 8 and a fourth bearing box 9 through lower cat claws, the middle pressure outer cylinder 3-1 is axially fixed with the bearing boxes by adopting a centering Liang Tuila mechanism, the middle pressure outer cylinder 3-1 and the fourth bearing box 9 expand towards the electric end direction of the middle pressure outer cylinder 3-1 by taking the third bearing box 8 as an absolute dead point, the first low pressure module 4 and the second low pressure module 5 expand towards the electric and regulating ends freely by taking the dead points of the first low pressure module 4 and the second low pressure module 5 as self dead points respectively, a thrust bearing is arranged on the second bearing box 7, the rotor takes the thrust bearing as a base point, the ultrahigh pressure rotor 1-6 expands towards the regulating end, namely the machine head direction, and the high pressure rotor 2-6, the middle pressure rotor 3-4, the low pressure rotor 4-5 and the low pressure rotor of the second low pressure module 5 expand towards the electric end direction. The other features are the same as in any one of the first to eighth embodiments.
Detailed description ten: referring to fig. 1 to 3, the ultra-high pressure module 1 and the high pressure module 2 of the present embodiment each adopt a2×180° tangential volute steam-intake structure, and are configured with horizontal vanes to ensure steam-intake efficiency. The ultra-high pressure module 1 and the high pressure module 2 are both in double-layer cylinder structures, the ultra-high pressure inner cylinder 1-2 and the high pressure inner cylinder 2-2 are both in regular cylindrical structures, the structure is simple and compact, the expansion is uniform, the thermal stress is small, and the quick start and stop of a unit and the load change adaptation requirements are facilitated. The ultra-high pressure inner cylinder 1-2 and the high pressure inner cylinder 2-2 adopt a red lantern ring sealing mode, are suitable for steam parameter design with higher pressure and temperature, have good sealing performance, are assembled in a modularized factory, are integrally shipped to the site, have strength check for more than 20 ten thousand hours, and can meet the 10-year overhaul period. The other features are the same as in any one of the first to ninth embodiments.
Eleventh embodiment: with reference to fig. 1 to 3, the middle pressure module 3 of the present embodiment adopts a2×180 ° tangential volute steam inlet structure, a double-layer cylinder and a symmetrical split design, the double-layer cylinder structure can effectively reduce the working temperature of the outer cylinder, save high temperature resistant materials and control the expansion amount of the outer cylinder, and meanwhile, the annular steam inlet chamber is also convenient to arrange, and the double split can effectively reduce the final stage blade height of the middle pressure cylinder, thereby improving the blade application maturity. The other features are the same as in any one of the embodiments.
Twelve specific embodiments: the embodiment is described by combining fig. 1 to 3, the first low-pressure module 4 and the second low-pressure module 5 of the embodiment adopt a 360-degree volute steam inlet type low-pressure integral cast iron inner cylinder, the rigidity is good, the deformation is small, the steam leakage loss caused by the middle division surface deformation is avoided, the volute steam inlet can effectively reduce the pressure loss at the inlet position, the efficiency of the low-pressure cylinder is improved, the inner cylinder is located at the outer cylinder supporting leg on the basis through the supporting arm, namely, the inner cylinder adopts a floor type structure, so that the inner cylinder is more suitable for large-range vacuum change and steam exhaust temperature change, and the rotor and stator parts can be always accurately centered. The other features are the same as in any one of the embodiments one to eleven.
Thirteen specific embodiments: referring to fig. 1, the ultra-high pressure rotor 1-6, the high pressure rotor 2-6, the low pressure rotor 4-5, and the low pressure rotor of the second low pressure module 5 are all integral forging rotors; the middle pressure rotor 3-4 adopts a modified FB2+2.25Cr welding structure, the middle of the middle pressure rotor 3-4 is made of modified FB2, the two ends of the middle pressure rotor 3-4 are made of 2.25Cr materials, the mechanical strength performance is different, the design of the steam inlet temperature at 630 ℃ is matched, and the application safety and reliability are higher. Other aspects are the same as in any one to twelve of the embodiments.
Fourteen specific embodiments: referring to fig. 1 to 3, the description of the present embodiment is given by way of illustration of the present embodiment, in which the through-flows of the ultra-high voltage module 1, the high voltage module 2, and the medium voltage module 3 are designed in a fully three-dimensional aerodynamic optimization according to the intake parameters, and the multi-stage reaction through-flow profile selection and the high-efficiency wide-load loading are performed, and the profile end wall optimization is equipped, so as to improve the through-flow aerodynamic efficiency and the variable-load adaptation characteristics. Except for the low-voltage end two-stage partition board, all static blades and moving blades of the other ultrahigh-voltage modules 1, the high-voltage modules 2, the medium-voltage modules 3, the first low-voltage modules 4 and the second low-voltage modules 5 adopt a pre-torsion assembly type structure, compared with the traditional welded partition board, the assembly type structure has no welding seams, through-flow deformation caused by welding and heat treatment after welding is avoided, the through-flow machining precision is higher, no operation welding thermal stress is released, long-term efficiency retention is better, and the aging rate of a unit is reduced. The other features are the same as in any one of the first to thirteenth embodiments.
Fifteen embodiments: referring to fig. 1 to 3, the present embodiment is described, in which the ultrahigh voltage module 1, the high voltage module 2, and the medium voltage module 3 all adopt an n+1 bearing support manner, so that the length of a shafting is shortened, the total length of a unit is shortened to the greatest extent on the premise that the unit has high circulation efficiency and high safety, the occupied area of the unit is reduced, the field space is saved, and the capital cost of an electric station is reduced. The other features are the same as in any one of the first to fourteenth embodiments.
Sixteen specific embodiments: referring to fig. 1 to 3, in this embodiment, the ultrahigh pressure module 1, the high pressure module 2, the medium pressure module 3, the first low pressure module 4 and the second low pressure module 5 of this embodiment all adopt a volute steam inlet technology, the valve is directly connected with an elastic support, the additional force to the cylinder is small, the valve adopts an excellent diffusion port runner design and is matched with a deceleration type volute runner, the circumferential uniformity of steam is improved to the greatest extent, the flow loss of steam at the inlet position is reduced, the steam pressure is prevented from being reduced outside the through flow, and the kinetic energy conversion efficiency of the steam is improved. The other features are the same as in any one to fifteen embodiments.
Seventeenth embodiment: referring to fig. 1 to 3, in the present embodiment, the intermediate stages of the through-flow of the ultrahigh-pressure module 1, the high-pressure module 2, and the medium-pressure module 3 do not need to design a regenerative extraction, so that the flow efficiency of steam in the through-flow is higher, and the efficiency of the ultrahigh-pressure module 1, the high-pressure module 2, and the medium-pressure module 3 can be further improved. Meanwhile, a primary high-pressure heater and a primary low-pressure heater are optimally added, the superheat degree of regenerative extraction steam at each stage is reduced, an external steam cooler can be omitted, and the circulation efficiency of a steam turbine thermodynamic system is remarkably improved. The design efficiency of the main circulation turbine is far higher than that of a conventional feed pump turbine, and the material consumption of a boiler reheater pipeline and the cost of a regenerative system are saved. The other features are the same as in any one to sixteen of the embodiments.
Working principle:
The main steam of the steam turbine enters a counter-flow ultrahigh pressure reaction pressure level through a steam inlet valve of an ultrahigh pressure module 1 from an outlet of a boiler superheater, after doing work, enters a primary reheater through a steam outlet on the lower half of an ultrahigh pressure outer cylinder 1-1, once-reheated steam enters a counter-flow high pressure level through a steam inlet valve of a forward high pressure module 2, after doing work, is discharged into a secondary reheater through a steam outlet on the lower half of the high pressure outer cylinder 2-1, the twice-reheated steam enters a part of a middle pressure module 3 through two high pressure main steam regulating joint valves 14 and two middle pressure main steam regulating joint valves 15 which are arranged on two sides of the middle pressure module 3, flows through a forward and reverse reaction middle pressure level through an outlet on the upper half of the middle pressure outer cylinder 3-1, after doing work, leaves the middle pressure outer cylinder 3-1, the outlet is respectively connected with the first low-pressure module 4 and the second low-pressure module 5 through a medium-low pressure communicating pipe 16, respectively enters the two completely same first low-pressure module 4 and the second low-pressure module 5, enters a condenser 11-3 through the lower exhaust ports of the exhaust cylinders of the first low-pressure module 4 and the second low-pressure module 5 after low pressure through flow, part of the exhaust steam of the ultra-high pressure module 1 enters the main circulation water supply pump turbine 11-1 through the main circulation water supply pump turbine inlet pipeline 11-2, part of the steam is extracted after 3 pressure levels of the main flow and enters the second high-pressure heater 11-15 through the second high-pressure heater exhaust pipeline 11-16, part of the steam is extracted after 4 pressure levels and enters the third high-pressure heater 11-17 through the third high-pressure heater exhaust pipeline 11-18, and then part of steam is extracted after 4 pressure stages and enters a fourth high-pressure heater 11-19 through a fourth high-pressure heater steam extraction pipeline 11-20, part of steam is extracted after 5 pressure stages and enters a fifth high-pressure heater 11-21 through a fifth high-pressure heater steam extraction pipeline 11-22, part of steam is extracted after 5 pressure stages and enters a deaerator 11-23 through a deaerator steam extraction pipeline 11-24, finally the steam is discharged after 4 pressure stages and enters a seventh low-pressure heater 11-25 through a main circulation water supply pump steam turbine steam extraction pipeline 11-26, and the rest of overflow steam enters a eighth low-pressure heater 11-29 through an overflow pipeline 11-28.
The present invention has been described in terms of preferred embodiments, but is not limited thereto, and any simple modification, equivalent variation and variation of the above embodiments according to the technical principles of the present invention will be within the scope of the present invention, as will be apparent to those skilled in the art without departing from the spirit and scope of the present invention.
Claims (7)
1. Novel 1000MW grade secondary reheat 630 ℃ steam turbine and supporting two quick-witted regenerative system, its characterized in that: the device comprises a steam turbine and a double-engine regenerative system (11);
the steam turbine is matched with a double-engine regenerative system (11);
The steam turbine comprises an ultrahigh pressure module (1), a high pressure module (2), a medium pressure module (3), a first low pressure module (4), a second low pressure module (5), a first bearing box (6), a second bearing box (7), a third bearing box (8), a fourth bearing box (9), a fifth bearing box (10), a sixth bearing box (11), a plurality of centering beams and a plurality of lower cylinder cat claws;
The electric end of the ultrahigh voltage module (1) is fixedly connected with one end of a first bearing box (6) through a centering beam, the electric end of the ultrahigh voltage module (1) is fixedly connected with one end of a second bearing box (7) through the centering beam, the other end of the second bearing box (7) is fixedly connected with one end of a high voltage module (2) through the centering beam, the electric end of the high voltage module (2) is in sliding contact with one end of a third bearing box (8) through a lower cylinder cat claw, the other end of the third bearing box (8) is in sliding contact with the regulating end of a middle voltage module (3) through a lower cylinder cat claw, the electric end of the middle voltage module (3) is fixedly connected with one end of a fourth bearing box (9) through the centering beam, the other end of the fourth bearing box (9) is fixedly connected with one end of a first low voltage module (4), the other end of the first low voltage module (4) is fixedly connected with one end of a fifth bearing box (10), the other end of the fifth bearing box (10) is fixedly connected with one end of a second low voltage module (5), and the other end of the second low voltage module (5) is fixedly connected with a sixth bearing box (11);
The double-machine heat recovery system (11) is respectively connected with the ultrahigh-pressure module (1), the medium-pressure module (3), the first low-pressure module (4) and the second low-pressure module (5) through pipelines, and the connection mode of the first low-pressure module (4) and the second low-pressure module (5) is the same as that of the double-machine heat recovery system (11);
the double-unit heat recovery system (11) comprises a first unit heat recovery system and a second unit heat recovery system;
The first unit heat recovery system comprises a condenser (11-3), a condenser steam inlet pipeline (11-4), a condensate pump, a gland seal cooler, a No. 9 low-pressure heater (11-5), a No. 9 low-pressure heater steam extraction pipeline (11-6), a No. 10 low-pressure heater (11-7), a No. 10 low-pressure heater steam extraction pipeline (11-8), a No. 11 low-pressure heater (11-9), a No. 11 low-pressure heater steam extraction pipeline (11-10), a No. 12 low-pressure heater (11-11) and a No. 12 low-pressure heater steam extraction pipeline (11-12);
The first low-pressure module (4) is connected with the No. 9 low-pressure heater (11-5) through a No. 9 low-pressure heater steam extraction pipeline (11-6), the first low-pressure module (4) is connected with the No. 10 low-pressure heater (11-7) through a No. 10 low-pressure heater steam extraction pipeline (11-8), the first low-pressure module (4) is connected with the No. 11 low-pressure heater (11-9) through a No. 11 low-pressure heater steam extraction pipeline (11-10), the first low-pressure module (4) is connected with the No. 12 low-pressure heater (11-11) through a No. 12 low-pressure heater steam extraction pipeline (11-12) and a No. 12 low-pressure heater (11-3), the first low-pressure module (4) is connected with the No. 11-3) through a condenser steam inlet pipeline (11-4), the No. 9 low-pressure heater (11-5), the No. 10 low-pressure heater (11-7), the No. 11 low-pressure heater (11-9), the No. 12 low-pressure heater (11-11), the condenser and the condenser (11-3) are sequentially connected to the condenser (11-3) along the two condenser systems (11-3) and the condenser through the condenser steam inlet pipeline steam pump (11-3;
The second unit regenerative system comprises a main circulation water supply pump turbine (11-1), a main circulation water supply pump turbine steam inlet pipeline (11-2), a first high-pressure heater (11-13), a first high-pressure heater steam extraction pipeline (11-14), a second high-pressure heater (11-15), a second high-pressure heater steam extraction pipeline (11-16), a third high-pressure heater (11-17), a third high-pressure heater steam extraction pipeline (11-18), a fourth high-pressure heater (11-19), a fourth high-pressure heater steam extraction pipeline (11-20), a fifth high-pressure heater (11-21), a fifth high-pressure heater steam extraction pipeline (11-22), a deaerator (11-23), a deaerator steam extraction pipeline (11-24), a seventh low-pressure heater (11-25), a main circulation water supply pump turbine steam extraction pipeline (11-26), an overflow regulating valve (11-27), an overflow pipeline (11-28) and an eighth low-pressure heater (11-29);
The ultra-high pressure module (1) is connected with the main circulation water supply pump steam turbine (11-1) through a main circulation water supply pump steam turbine steam inlet pipeline (11-2), the ultra-high pressure module (1) is connected with a first high pressure heater (11-13) through an ultra-high pressure exhaust pipeline in the ultra-high pressure module (1), the main circulation water supply pump steam turbine (11-1) is respectively connected with a second high pressure heater steam outlet pipeline (11-16), a third high pressure heater steam outlet pipeline (11-18), a fourth high pressure heater steam outlet pipeline (11-20), a fifth high pressure heater steam outlet pipeline (11-22), a deaerator steam outlet pipeline (11-24), a main circulation water supply pump steam turbine steam outlet pipeline (11-26), an overflow pipeline (11-28) and a second high pressure heater (11-15), a third high pressure heater (11-17), a fourth high pressure heater (11-19), a fifth high pressure heater (11-21), a deaerator (11-23), a seventh low pressure heater (11-25) and an eight high pressure heater (11-27) through an overflow valve (11-27) which is connected with the overflow valve (11-11), the medium-pressure module (3) is connected with a eighth low-pressure heater (11-29) through a medium-pressure exhaust pipeline in the medium-pressure module (3), the first high-pressure heater (11-13) is connected with a boiler through a first high-pressure heater steam extraction pipeline (11-14), the first high-pressure heater (11-13), the second high-pressure heater (11-15), the third high-pressure heater (11-17), the fourth high-pressure heater (11-19), the fifth high-pressure heater (11-21), the deaerator (11-23), the seventh low-pressure heater (11-25), the eighth low-pressure heater (11-29) and the 9 low-pressure heater (11-5) are sequentially connected from right to left along the length direction of the double-machine regenerative system (11);
The ultrahigh pressure module (1) comprises an ultrahigh pressure outer cylinder (1-1), an ultrahigh pressure inner cylinder (1-2), an ultrahigh pressure steam exhaust side end steam seal (1-3), an ultrahigh pressure steam inlet side end steam seal (1-4), an ultrahigh pressure balance drum steam seal (1-5), an ultrahigh pressure rotor (1-6), an ultrahigh pressure moving blade and an ultrahigh pressure stationary blade;
The inside of the ultra-high pressure outer cylinder (1-1) is provided with an ultra-high pressure inner cylinder (1-2), an ultra-high pressure rotor (1-6) is arranged at the inner horizontal center of the ultra-high pressure inner cylinder (1-2), an ultra-high pressure exhaust side steam seal (1-3) is assembled at the end adjusting end of the ultra-high pressure outer cylinder (1-1), an ultra-high pressure inlet side steam seal (1-4) is assembled at the electric end of the ultra-high pressure outer cylinder (1-1), an ultra-high pressure balance drum steam seal (1-5) is assembled at the electric end of the ultra-high pressure inner cylinder (1-2), and ultra-high pressure moving blades and ultra-high pressure stationary blades are respectively assembled on the ultra-high pressure rotor (1-6) and the ultra-high pressure inner cylinder (1-2).
2. The novel 1000MW grade secondary reheating 630 ℃ steam turbine and matched double-machine regenerative system as claimed in claim 1, wherein the novel 1000MW grade secondary reheating 630 ℃ steam turbine and matched double-machine regenerative system are characterized in that: the system also comprises two ultrahigh-pressure main steam regulating and supplementing combined valves (13), two high-pressure main steam regulating combined valves (14) and two medium-pressure main steam regulating combined valves (15);
The two ultrahigh-pressure main steam regulating and supplementing combined valves (13) are symmetrically arranged on two sides of the ultrahigh-pressure module (1) respectively, the two high-pressure main steam regulating combined valves (14) are symmetrically arranged on two sides of the ultrahigh-pressure module (1) respectively in the high-pressure module (2), and the two medium-pressure main steam regulating combined valves (15) are symmetrically arranged on two sides of the medium-pressure module (3) respectively.
3. The novel 1000MW grade secondary reheating 630 ℃ steam turbine and matched double-machine regenerative system as claimed in claim 1, wherein the novel 1000MW grade secondary reheating 630 ℃ steam turbine and matched double-machine regenerative system are characterized in that: the high-pressure module (2) comprises a high-pressure outer cylinder (2-1), a high-pressure inner cylinder (2-2), a high-pressure steam exhaust side end steam seal (2-3), a high-pressure steam inlet side end steam seal (2-4), a high-pressure balance drum steam seal (2-5), a high-pressure rotor (2-6), high-pressure moving blades and high-pressure stationary blades;
the high-pressure inner cylinder (2-2) is arranged in the high-pressure outer cylinder (2-1), the high-pressure rotor (2-6) is arranged in the inner horizontal center of the high-pressure inner cylinder (2-2) and is concentric with the ultrahigh-pressure rotor (1-6), the high-pressure steam inlet side steam seal (2-4) is assembled at the end of the high-pressure outer cylinder (2-1), the high-pressure steam outlet side steam seal (2-3) is assembled at the electric end of the high-pressure outer cylinder (2-1), the high-pressure balance drum steam seal (2-5) is assembled at the end of the high-pressure outer cylinder (2-1), and the high-pressure moving blades and the high-pressure stationary blades are respectively assembled on the high-pressure rotor (2-6) and the high-pressure inner cylinder (2-2).
4. The novel 1000MW grade secondary reheating 630 ℃ steam turbine and matched double-machine regenerative system as claimed in claim 1, wherein the novel 1000MW grade secondary reheating 630 ℃ steam turbine and matched double-machine regenerative system are characterized in that: the medium pressure module (3) comprises a medium pressure outer cylinder (3-1), a medium pressure inner cylinder (3-2), two medium pressure exhaust side end steam seals (3-3), a medium pressure rotor (3-4), a medium pressure positive direction moving blade and a medium pressure positive direction stationary blade;
an intermediate pressure inner cylinder (3-2) is arranged in the intermediate pressure outer cylinder (3-1), an intermediate pressure rotor (3-4) is arranged in the inner horizontal center of the intermediate pressure inner cylinder (3-2), the intermediate pressure rotor (3-4) is concentrically arranged with an ultrahigh pressure rotor (1-6) and a high pressure rotor (2-6), one intermediate pressure exhaust side steam seal (3-3) is arranged at the end of the intermediate pressure outer cylinder (3-1), the other intermediate pressure exhaust side steam seal (3-3) is arranged at the electric end of the intermediate pressure outer cylinder (3-1), and an intermediate pressure positive direction moving blade and an intermediate pressure positive direction stationary blade are respectively assembled on the intermediate pressure rotor (3-4) and the intermediate pressure inner cylinder (3-2).
5. The novel 1000MW grade secondary reheating 630 ℃ steam turbine and matched double-machine regenerative system as claimed in claim 1, wherein the novel 1000MW grade secondary reheating 630 ℃ steam turbine and matched double-machine regenerative system are characterized in that: the first low-voltage module (4) and the second low-voltage module (5) have the same structure;
The first low-pressure module (4) comprises a low-pressure outer cylinder (4-1), a low-pressure inner cylinder (4-2), two low-pressure exhaust side end steam seals (4-3), two end corrugated sections (4-4), a low-pressure rotor (4-5), a low-pressure square moving blade, a low-pressure square stationary blade and a partition sleeve;
The low-pressure outer cylinder (4-1) is internally provided with a low-pressure inner cylinder (4-2), the low-pressure inner cylinder (4-2) is internally provided with a low-pressure rotor (4-5), one low-pressure exhaust side end steam seal (4-3) and one end corrugated joint (4-4) are sequentially arranged at the end of the low-pressure outer cylinder (4-1), the other end corrugated joint (4-4) and one low-pressure exhaust side end steam seal (4-3) are sequentially arranged at the electric end of the low-pressure outer cylinder (4-1), and the low-pressure square moving blades and the low-pressure square stationary blades are respectively assembled on the low-pressure rotor (4-5), the low-pressure inner cylinder and the partition plate sleeve.
6. The novel 1000MW grade double reheat 630 ℃ steam turbine and matched double heat recovery system according to claim 1 or 5, wherein: it also comprises a medium-low pressure communicating pipe (16),
The medium-low pressure communicating pipe (16) is arranged right above the medium-pressure module (3), the fourth bearing box (9), the first low pressure module (4), the fifth bearing box (10) and the second low pressure module (5);
The medium-low pressure communicating pipe (16) comprises a first connecting pipe (16-1), a second connecting pipe (16-2), a third connecting pipe (16-3), a fourth connecting pipe (16-4) and a straight pipe (16-5);
the first connecting pipe (16-1), the second connecting pipe (16-2), the third connecting pipe (16-3), the fourth connecting pipe (16-4) and the straight pipe (16-5) are integrated;
The first connecting pipe (16-1), the second connecting pipe (16-2), the third connecting pipe (16-3) and the fourth connecting pipe (16-4) are all arranged below the straight pipe (16-5), the first connecting pipe (16-1) is connected with the adjusting end of the middle-pressure outer cylinder (3-1) and communicated with each other, the second connecting pipe (16-2) is connected with the electric end of the middle-pressure outer cylinder (3-1) and communicated with each other, the third connecting pipe (16-3) is connected with the middle part of the low-pressure outer cylinder (4-1) and communicated with each other, and the fourth connecting pipe (16-4) is connected with the middle part of the low-pressure outer cylinder of the second low-pressure module (5) and communicated with each other.
7. The novel 1000MW grade secondary reheating 630 ℃ steam turbine and matched double-machine regenerative system as claimed in claim 1, wherein the novel 1000MW grade secondary reheating 630 ℃ steam turbine and matched double-machine regenerative system are characterized in that: the steam turbine also includes a thrust bearing,
The thrust bearing is arranged on the second bearing box (7), and the absolute dead points are respectively positioned at the intersection points of the transverse positioning key and the longitudinal positioning key at the bottoms of the first low-pressure module (4), the middle of the second low-pressure module (5) and the third bearing box (8).
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| CN104456519B (en) * | 2014-11-03 | 2016-08-17 | 章礼道 | A kind of new and effective water supply heat back system for double reheat power generation sets |
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| CN210530935U (en) * | 2019-07-17 | 2020-05-15 | 山东电力工程咨询院有限公司 | Double-machine regenerative system with multiple shafts arranged |
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