CN107246286B - Single reheat steam turbine of parallelly connected high pressure cylinder - Google Patents
Single reheat steam turbine of parallelly connected high pressure cylinder Download PDFInfo
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- CN107246286B CN107246286B CN201710533199.8A CN201710533199A CN107246286B CN 107246286 B CN107246286 B CN 107246286B CN 201710533199 A CN201710533199 A CN 201710533199A CN 107246286 B CN107246286 B CN 107246286B
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- 238000000605 extraction Methods 0.000 claims abstract description 51
- 238000003303 reheating Methods 0.000 claims abstract description 8
- 230000001105 regulatory effect Effects 0.000 claims description 36
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 description 20
- 230000001360 synchronised effect Effects 0.000 description 6
- 230000001172 regenerating effect Effects 0.000 description 5
- 238000009834 vaporization Methods 0.000 description 5
- 230000008016 vaporization Effects 0.000 description 5
- 238000010586 diagram Methods 0.000 description 4
- 238000010248 power generation Methods 0.000 description 3
- 230000007423 decrease Effects 0.000 description 2
- 238000010438 heat treatment Methods 0.000 description 2
- 238000012986 modification Methods 0.000 description 2
- 230000004048 modification Effects 0.000 description 2
- 238000006467 substitution reaction Methods 0.000 description 2
- 230000007547 defect Effects 0.000 description 1
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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steam systems, cycles or processes; Control means specially adapted for such systems, cycles or processes; Use of withdrawn or exhaust steam for feed-water heating
- F01K7/16—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steam systems, cycles or processes; Control means specially adapted for such systems, cycles or processes; Use of withdrawn or exhaust steam for feed-water heating the engines being only of turbine type
- F01K7/22—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 only of turbine type the turbines having inter-stage steam heating
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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
- F01K11/00—Plants characterised by the engines being structurally combined with boilers or condensers
- F01K11/02—Plants characterised by the engines being structurally combined with boilers or condensers the engines being turbines
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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
- F01K17/00—Using steam or condensate extracted or exhausted from steam engine plant
- F01K17/02—Using steam or condensate extracted or exhausted from steam engine plant for heating purposes, e.g. industrial, domestic
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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
- F01K7/16—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 only of turbine type
- F01K7/22—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 only of turbine type the turbines having inter-stage steam heating
- F01K7/24—Control or safety means specially adapted therefor
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- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Control Of Turbines (AREA)
Abstract
The invention relates to the technical field of steam turbines, in particular to a single reheating steam turbine with parallel high-pressure cylinders, which comprises a main steam turbine system and an auxiliary high-pressure cylinder, wherein the main steam turbine system comprises a high-pressure cylinder, a middle-pressure cylinder, a low-pressure cylinder and a reheater, a steam inlet of the high-pressure cylinder is communicated with a high-pressure steam pipeline, and a steam outlet is communicated with an inlet of the reheater through a cold reheating steam pipeline; the steam inlet of the auxiliary high-pressure cylinder is communicated with the high-pressure steam pipeline through an auxiliary steam inlet pipeline, the steam outlet is communicated with the cold reheating steam pipeline through an auxiliary steam outlet pipeline, and an auxiliary steam inlet valve group is arranged on the auxiliary steam inlet pipeline; the outlet of the reheater is communicated with the steam inlet of the intermediate pressure cylinder through a hot reheat steam pipeline; the high-pressure cylinder is provided with a high-pressure steam extraction port, the high-pressure steam extraction port is connected with a first steam extraction pipeline leading to a first heater, and the first heater is connected with a first bypass in parallel. The economy of the partial load working condition can be improved, meanwhile, the economy of the high load working condition is improved, and the economy of the rated load is guaranteed.
Description
Technical Field
The invention relates to the technical field of steam turbines, in particular to a single reheating steam turbine with parallel high-pressure cylinders.
Background
In recent years, under the influence of macroscopic economy, the increase of the power consumption at a low speed becomes a normal state, and meanwhile, the capacity of a power grid in China is continuously enlarged, the energy structure is continuously adjusted, and the proportion of renewable energy resources is steadily increased. In order to ensure the basic load of renewable energy, the thermal power generating unit participates in deep peak shaving, and the operation under the low-load working condition for a long time is a necessary trend. The design key points of the thermal power generating unit are changed, and the high efficiency of the basic load is ensured from the original high efficiency, and the high efficiency of the unit at the full load is ensured.
At present, the domestic power industry applies three different design specifications to define the capacity of a steam turbine: the standard of the original electric power department industry is DL/T892-2004, the national standard GB5578-2007 and the international IEC 60045-1. Among them, the DL/T892-2004 standard proposes a specification defining the capacity of the unit in terms of extreme high back pressure in summer of 11.8kPa (a): (1) the nameplate output is a summer working condition (TRL); (2) maximum continuous output condition (TMCR); (3) a heat rate acceptance condition (THA); (4) a valve full open condition (VWO); the maximum capacity of the through-flow design is about 112% -113% of the rated operating conditions. The GB5578-2007 standard proposes a specification defining the capacity of a unit according to the local summer back pressure: (1) nameplate output, maximum guaranteed output and heat rate guarantee are combined into the same working condition (TMCR); (2) summer conditions (TRL); (3) a valve full open condition (VWO); the maximum capacity of the through-flow design is about 108% -110% of the rated operating condition. IEC60045-1 defines the capacity of a unit with maximum guaranteed continuous power: (1) nameplate output, maximum guaranteed output and heat rate guarantee are combined into the same working condition (TMCR); (2) a valve full open condition (VWO); the maximum capacity of the through-flow design is about 103% -105% of the rated operating condition. The steam turbine configured according to the current design specification can already send out rated output at the minimum of 87% of through-flow capacity, and the unit operates under partial load for a long time, so that the economical efficiency of the unit is obviously reduced. Along with the continuous decline of the annual service hours of thermal power generating unit, the economic nature decline of unit is more obvious.
In the prior art, in order to improve the economical efficiency of a unit under low load, the power generation capacity of a steam turbine under the design working condition is reduced to 83% -95% of rated output, and the steam turbine unit can reach rated main steam pressure under the working condition lower than the rated load. Correspondingly, the main steam pressure, the regenerative steam extraction pressure and the final water supply temperature of the partial load are all improved, and the overall economy of the partial load is improved. Meanwhile, the output of the steam turbine under the through-flow capacity is improved by adopting the technical means of heater bypass adjustment and the overpressure operation of the steam turbine, and the requirement of the rated output of the steam turbine is met.
As shown in fig. 1, which is a schematic structural diagram of the above-mentioned conventional steam turbine, high-pressure steam in a boiler 01 enters a high-pressure cylinder HP of the steam turbine through a regulating valve group 02, the high-pressure cylinder HP is provided with a steam extraction port, the steam is extracted from the steam extraction port, and feed water is heated by a heater 031, so that latent heat of vaporization is recovered. The exhaust steam of the high pressure cylinder HP is led to the reheater 04, heated and heated, and then enters the intermediate pressure cylinder IP. The intermediate pressure cylinder IP is provided with two steam extraction ports, from which steam is extracted, and the steam is heated by the heater 033 and the heater 034, respectively, to recover latent heat of vaporization. The exhaust steam of intermediate pressure cylinder IP is led to first low pressure cylinder LP1 and second low pressure cylinder LP 2. Meanwhile, the exhaust steam of the high pressure cylinder HP and the medium pressure cylinder IP is heated feed water or supplied to other users through the heater 032 and the heater 035, respectively. The heater 031, the heater 032, the heater 033 and the heater 034 are connected in parallel to a bypass, respectively. The unit delivers electrical energy to the grid through generator 05.
Due to the adoption of the scheme, the maximum capacity of the through-flow design of the steam turbine unit is reduced, so that the economy of the unit at partial load is improved. Meanwhile, in order to meet the power generation capacity of the steam turbine unit, the bypass is required to be put into the steam turbine unit in sequence, the final water supply temperature and the thermodynamic cycle efficiency are reduced, and the economical efficiency of the steam turbine unit under a high-load working condition is obviously reduced.
Disclosure of Invention
The invention aims to solve the technical problem of providing a single reheat steam turbine with parallel high pressure cylinders, which can improve the partial load economy, has the rated load generating capacity and can ensure the full load economy, so as to overcome the defects in the prior art.
In order to solve the technical problems, the invention adopts the following technical scheme: a single reheating turbine with parallel high-pressure cylinders comprises a main turbine system and an auxiliary high-pressure cylinder, wherein the main turbine system comprises a high-pressure cylinder, a middle-pressure cylinder, a low-pressure cylinder and a reheater, a steam inlet of the high-pressure cylinder is communicated with a high-pressure steam pipeline, and a steam outlet is communicated with an inlet of the reheater through a cold reheating steam pipeline; the steam inlet of the auxiliary high-pressure cylinder is communicated with the high-pressure steam pipeline through an auxiliary steam inlet pipeline, the steam outlet is communicated with the cold reheating steam pipeline through an auxiliary steam outlet pipeline, and an auxiliary steam inlet valve group is arranged on the auxiliary steam inlet pipeline; the outlet of the reheater is communicated with the steam inlet of the intermediate pressure cylinder through a hot reheat steam pipeline; the high-pressure cylinder is provided with a high-pressure steam extraction port, the high-pressure steam extraction port is connected with a first steam extraction pipeline leading to a first heater, and the first heater is connected with a first bypass in parallel.
Preferably, a first regulating valve group is arranged on the first bypass.
Preferably, a second steam extraction pipeline leading to a second heater is connected to the steam outlet of the high-pressure cylinder, and the second heater is connected with a second bypass in parallel.
Preferably, a second regulating valve group is arranged on the second bypass.
Preferably, a high-pressure steam inlet valve group is arranged at the steam inlet of the high-pressure cylinder.
Preferably, the intermediate pressure cylinder is provided with a first intermediate pressure steam extraction port and a second intermediate pressure steam extraction port, the first intermediate pressure steam extraction port and the second intermediate pressure steam extraction port are respectively connected with a third steam extraction pipeline leading to a third heater and a fourth steam extraction pipeline leading to a fourth heater, and the third heater and the fourth heater are respectively connected with a third bypass and a fourth bypass in parallel.
Preferably, a third regulating valve group and a fourth regulating valve group are respectively arranged on the third bypass and the fourth bypass.
Preferably, the main turbine system adopts a single-shaft arrangement, and the auxiliary high-pressure cylinder and the main turbine system are arranged in a split-shaft manner; and a rotor output shaft of the high-pressure cylinder or the low-pressure cylinder is provided with a first generator, and a rotor output shaft of the auxiliary high-pressure cylinder is provided with a second generator.
Preferably, the main turbine system adopts a single-shaft arrangement, and the auxiliary high-pressure cylinder is connected with a rotor shaft of the high-pressure cylinder through an automatic synchronous clutch; and a first generator is arranged on the rotor output shaft of the low pressure cylinder.
Preferably, the high-pressure cylinder and the intermediate-pressure cylinder are arranged in a split-shaft manner, the intermediate-pressure cylinder and the low-pressure cylinder are arranged coaxially, and the auxiliary high-pressure cylinder is connected with a rotor shaft of the high-pressure cylinder through an automatic synchronous clutch; and a rotor output shaft of the intermediate pressure cylinder or the low pressure cylinder is provided with a first generator, and a rotor output shaft of the high pressure cylinder is provided with a second generator.
Compared with the prior art, the invention has the remarkable progress that:
by arranging the auxiliary high-pressure cylinder, the maximum capacity of the through-flow design of the high-pressure cylinder of the main turbine system can be further reduced, and the main steam pressure, the regenerative steam extraction pressure and the final water supply temperature under the partial load working condition are improved, so that the economy of the partial load working condition is improved. Meanwhile, the auxiliary high-pressure cylinder and the heater bypass are combined, so that the economy of the unit under a high-load working condition can be improved, and the economy of a rated-load working condition is ensured on the basis of increasing the capacity of the unit. Therefore, the single reheat steam turbine with the parallel high-pressure cylinders can improve the economical efficiency of thermodynamic cycle, and particularly can improve the overall economical efficiency of a unit under wide and low load working conditions.
Drawings
FIG. 1 is a schematic representation of a prior art steam turbine.
Fig. 2 is a first structural schematic diagram of the single reheat steam turbine connected in parallel with the high pressure cylinder according to the embodiment of the present invention.
Fig. 3 is a second configuration diagram of the single reheat steam turbine connected in parallel with the high pressure cylinder according to the embodiment of the present invention.
Fig. 4 is a third schematic diagram of the single reheat steam turbine with parallel high pressure cylinders according to the embodiment of the present invention.
In the figure:
HP, high-pressure cylinder HP1, high-pressure cylinder HP2 and auxiliary high-pressure cylinder
IP, middle pressure cylinder LP1, first low pressure cylinder LP2, second low pressure cylinder
100. High-pressure steam pipeline 200, cold reheat steam pipeline 300 and auxiliary steam inlet pipeline
400. Auxiliary steam exhaust pipeline 500, hot reheat steam pipeline 600 and medium pressure steam pipeline
701. A first extraction steam pipeline 702, a second extraction steam pipeline 703 and a third extraction steam pipeline
704. A fourth extraction conduit 705, a fifth extraction conduit 801, a first bypass
802. Second bypass 803, third bypass 804, fourth bypass
01. Boiler 02, adjusting valve group 031, heater
032. Heater 033, heater 034, and heater
035. Heater 04, reheater 05, generator
1. Boiler 21, auxiliary steam inlet valve group 22 and high-pressure steam inlet valve group
31. First heater 32, second heater 33, third heater
34. Fourth heater 35, fifth heater 4, reheater
51. A first, a second and a third regulating valve group 52, 53
54. A fourth regulating valve group 61, a first generator 62 and a second generator
7. Automatic synchronous clutch
Detailed Description
The following describes embodiments of the present invention in further detail with reference to the accompanying drawings. These embodiments are merely illustrative of the present invention and are not intended to limit the present invention.
In the description of the present invention, it should be noted that the terms "first", "second", "third", "fourth" and "fifth" are used for descriptive purposes only and are not to be construed as indicating or implying relative importance. Unless expressly stated or limited otherwise, the terms "mounted," "connected," and "connected" are intended to be inclusive and mean, for example, that they may be fixedly connected, detachably connected, or integrally connected; can be mechanically or electrically connected; they may be connected directly or indirectly through intervening media, or they may be interconnected between two elements. The specific meanings of the above terms in the present invention can be understood by those skilled in the art according to specific situations. "plurality" means two or more.
As shown in fig. 2 to 4, an embodiment of the single reheat steam turbine of the parallel high pressure cylinder of the present invention. As shown in fig. 2, the single reheat turbine with parallel high-pressure cylinders of the present embodiment includes a main turbine system and an auxiliary high-pressure cylinder HP2, the main turbine system includes a high-pressure cylinder HP1, an intermediate-pressure cylinder IP, a low-pressure cylinder, and a reheater 4, and the low-pressure cylinder in the present embodiment is provided with two: first low pressure cylinder LP1 and second low pressure cylinder LP 2.
The steam inlet of the high-pressure cylinder HP1 is communicated with a high-pressure steam pipeline 100, and high-pressure steam is introduced into the high-pressure cylinder HP1 through the high-pressure steam pipeline 100. A high pressure steam conduit 100 may be in communication with an outlet of the boiler 1 for introducing high pressure steam from the boiler 1 into the high pressure cylinder HP 1. Preferably, a high-pressure steam inlet valve group 22 is arranged at a steam inlet of the high-pressure cylinder HP1, and the flow of high-pressure steam entering the high-pressure cylinder HP1 can be adjusted and controlled by adjusting the opening of the high-pressure steam inlet valve group 22. The steam outlet of high-pressure cylinder HP1 is connected to the inlet of reheater 4 via cold reheat steam line 200, and the steam discharged from the steam outlet of high-pressure cylinder HP1 is introduced into reheater 4 via cold reheat steam line 200 and reheated by reheater 4.
The steam inlet of the auxiliary high-pressure cylinder HP2 is communicated with the high-pressure steam pipeline 100 through an auxiliary steam inlet pipeline 300, an auxiliary steam inlet valve group 21 is arranged on the auxiliary steam inlet pipeline 300, and when the auxiliary steam inlet valve group 21 is opened, part of high-pressure steam in the high-pressure steam pipeline 100 can be introduced into the auxiliary high-pressure cylinder HP2 through the auxiliary steam inlet pipeline 300; when the auxiliary steam inlet valve group 21 is closed, no high-pressure steam flows into the auxiliary high-pressure cylinder HP 2. Further, by adjusting the opening of the auxiliary steam intake valve group 21, the flow rate of the high-pressure steam flowing into the auxiliary high-pressure cylinder HP2 can be adjusted and controlled. The steam outlet of auxiliary high pressure cylinder HP2 is in communication with cold reheat steam line 200 via an auxiliary steam exhaust line 400, and steam exhausted from the steam outlet of auxiliary high pressure cylinder HP2 is directed by auxiliary steam exhaust line 400 into cold reheat steam line 200. When the auxiliary steam intake valve group 21 is opened, steam discharged from the steam outlet of the auxiliary high-pressure cylinder HP2 and steam discharged from the steam outlet of the high-pressure cylinder HP1 are mixed in the cold reheat steam pipe 200, and then enter the reheater 4 to be reheated by the reheater 4.
The outlet of the reheater 4 is connected to the steam inlet of the intermediate pressure cylinder IP via a hot reheat steam line 500, and the steam reheated in the reheater 4 is introduced into the intermediate pressure cylinder IP via the hot reheat steam line 500. The steam outlet of intermediate pressure cylinder IP is communicated with the steam inlet of first low pressure cylinder LP1 and the steam inlet of second low pressure cylinder LP2 through intermediate pressure steam pipe 600, and the steam discharged from the steam outlet of intermediate pressure cylinder IP is introduced into first low pressure cylinder LP1 and second low pressure cylinder LP2 by intermediate pressure steam pipe 600.
The high pressure cylinder HP1 is provided with a high pressure steam extraction opening, the high pressure steam extraction opening is connected with a first steam extraction pipe 701 leading to the first heater 31, and the first heater 31 is connected in parallel with the first bypass 801. The latent heat of vaporization can be recovered by heating the feedwater by the first heater 31. When the first bypass 801 is put into use, part of the feed water leaves the first bypass 801, and the feed water amount passing through the first heater 31 can be reduced, so that the steam extraction demand in the first steam extraction pipe 701 is reduced, and the output of the unit is increased. Preferably, the first bypass 801 is provided with the first regulating valve group 51, the opening of the first regulating valve group 51 is gradually increased, so that the flow rate of the water fed into the first bypass 801 can be slowly increased, the safety and the flexibility are better, and the load required by the unit can be achieved by regulating the flow rate of the water fed into the first bypass 801.
Further, a second extraction conduit 702 leading to the second heater 32 is connected to the outlet of the high pressure cylinder HP1, the second heater 32 being connected in parallel with the second bypass 802. Similarly, the latent heat of vaporization can be recovered by heating the feed water by the second heater 32. When the second bypass 802 is put into use, part of the feed water leaves the second bypass 802, and the feed water amount passing through the second heater 32 can be reduced, thereby reducing the steam extraction demand in the second steam extraction pipe 702 and further increasing the output of the unit. Preferably, the second bypass 802 is provided with the second regulating valve group 52, the water supply flow entering the second bypass 802 can be slowly increased through the gradual increase of the opening degree of the second regulating valve group 52, the safety and the flexibility are better, and the load required by the unit can be achieved by regulating the water supply flow entering the second bypass 802.
The single reheat steam turbine of the parallel high-pressure cylinder of the embodiment can further reduce the maximum capacity of the through-flow design of the high-pressure cylinder HP1 of the main steam turbine system by arranging the auxiliary high-pressure cylinder HP2, and improves the main steam pressure, the regenerative steam extraction pressure and the final water supply temperature under the partial load working condition, thereby improving the economy of the partial load working condition. Meanwhile, the auxiliary high-pressure cylinder HP2 is combined with the heater bypass adjustment, so that the economy of the unit under the high-load working condition can be improved, and the economy of the rated-load working condition is guaranteed on the basis of increasing the capacity of the unit. Therefore, the single reheat steam turbine with the high-pressure cylinders connected in parallel can improve the economical efficiency of thermodynamic cycle, and especially can improve the overall economical efficiency of a unit under wide and low load working conditions. Specifically, in actual operation, with the gradual increase of the unit load, the single reheat steam turbine of the parallel high-pressure cylinder of the embodiment can sequentially realize the following five operation modes:
in the first operation mode, the auxiliary steam inlet valve group 21 is closed, all high-pressure steam entering the high-pressure steam pipeline 100 from the outlet of the boiler 1 enters the high-pressure cylinder HP1 of the main turbine system through the high-pressure steam inlet valve group 22, no high-pressure steam flows into the auxiliary high-pressure cylinder HP2, the first regulating valve group 51 and the second regulating valve group 52 are both closed, and the first bypass 801 and the second bypass 802 are not used.
In the second operation mode, the auxiliary steam inlet valve group 21 is closed, all high-pressure steam entering the high-pressure steam pipeline 100 from the outlet of the boiler 1 enters the high-pressure cylinder HP1 of the main turbine system through the high-pressure steam inlet valve group 22, no high-pressure steam flows into the auxiliary high-pressure cylinder HP2, the first regulating valve group 51 is opened, the first bypass 801 is put into use, the second regulating valve group 52 is closed, and the second bypass 802 is not put into use.
In the third operation mode, the auxiliary steam inlet valve group 21 is closed, all high-pressure steam entering the high-pressure steam pipeline 100 from the outlet of the boiler 1 enters the high-pressure cylinder HP1 of the main turbine system through the high-pressure steam inlet valve group 22, no high-pressure steam flows into the auxiliary high-pressure cylinder HP2, the first regulating valve group 51 and the second regulating valve group 52 are both opened, and the first bypass 801 and the second bypass 802 are both put into use.
In the fourth operation mode, the auxiliary steam inlet valve group 21 is opened, a part of high-pressure steam entering the high-pressure steam pipeline 100 from the outlet of the boiler 1 enters the high-pressure cylinder HP1 of the main turbine system through the high-pressure steam inlet valve group 22, the other part of high-pressure steam enters the auxiliary high-pressure cylinder HP2 through the auxiliary steam inlet valve group 21, the first adjusting valve group 51 and the second adjusting valve group 52 are both closed, and the first bypass 801 and the second bypass 802 are not used.
In the fifth operation mode, the auxiliary steam inlet valve group 21 is opened, a part of high-pressure steam entering the high-pressure steam pipeline 100 from the outlet of the boiler 1 enters the high-pressure cylinder HP1 of the main turbine system through the high-pressure steam inlet valve group 22, the other part enters the auxiliary high-pressure cylinder HP2 through the auxiliary steam inlet valve group 21, the first regulating valve group 51 is opened, the first bypass 801 is put into use, the second regulating valve group 52 is closed, and the second bypass 802 is not put into use.
When the load required by the unit is smaller than the maximum capacity of the through-flow design of the main steam turbine system, only the main steam turbine system can meet the load requirement of the unit, and at the moment, the first operation mode can be selected, and as the maximum capacity of the through-flow design of the high-pressure cylinder HP1 of the main steam turbine system is reduced, the main steam pressure, the regenerative steam extraction pressure and the final water supply temperature under the partial load working condition can be improved, so that the overall economy under the partial load working condition is improved. When the load required by the unit is slightly larger than the maximum capacity of the through-flow design of the main turbine system, if the auxiliary steam inlet valve group 21 is opened, the flow rate of high-pressure steam entering the auxiliary high-pressure cylinder HP2 is small, and the deviation from the design point of the auxiliary high-pressure cylinder HP2 is large, so that the economy is reduced, therefore, the operation mode two or the operation mode three can be selected according to the size of the load required by the actual unit, and the water feeding flow rates entering the first bypass 801 and the second bypass 802 are adjusted through the first adjusting valve group 51 and the second adjusting valve group 52 to meet the load requirement required by the unit. When the load required by the unit is close to the rated output of the unit, the operation mode four can be selected, and at the moment, the main turbine system and the auxiliary high-pressure cylinder HP2 both operate at a point close to the design point, so that the economy of the unit is ensured. When the required load of the unit is larger than the rated output of the unit, the fifth operation mode can be selected, at the moment, the main turbine system and the auxiliary high-pressure cylinder HP2 both operate at a point close to the design point, and the actual output of the unit is increased by using the first bypass 801, so that the required load requirement is met.
Further, the intermediate pressure cylinder IP of this embodiment is provided with a first intermediate pressure steam extraction port and a second intermediate pressure steam extraction port, the first intermediate pressure steam extraction port and the second intermediate pressure steam extraction port on the intermediate pressure cylinder IP are respectively connected with a third steam extraction pipeline 703 leading to the third heater 33 and a fourth steam extraction pipeline 704 leading to the fourth heater 34, and the steam exhaust port of the intermediate pressure cylinder IP is connected with a fifth steam extraction pipeline 705 leading to the fifth heater 35. The feed water is heated by the third heater 33, the fourth heater 34, and the fifth heater 35, and latent heat of vaporization can be recovered.
The third heater 33 and the fourth heater 34 in the present embodiment are connected in parallel to the third bypass 803 and the fourth bypass 804, respectively. Preferably, a third regulating valve group 53 and a fourth regulating valve group 54 are respectively arranged on the third bypass 803 and the fourth bypass 804. Because the auxiliary high-pressure cylinder HP2 is arranged in the single reheat steam turbine of the parallel high-pressure cylinder in the embodiment, the rated load generating capacity of the unit is realized by the cooperation of the auxiliary high-pressure cylinder HP2 and the first bypass 801 and the second bypass 802, the output of the unit does not need to be increased by using the third bypass 803 and the fourth bypass 804 in actual normal operation, and only when the third heater 33 or the fourth heater 34 fails, the third regulating valve group 53 or the fourth regulating valve group 54 needs to be opened, so that feed water passes through the third bypass 803 or the fourth bypass 804, and the normal operation of the unit is ensured.
In the present embodiment, the first heater 31, the second heater 32, the third heater 33, and the fourth heater 34 are surface high-pressure heaters, and the fifth heater 35 is a hybrid heater.
In this embodiment, the arrangement form of the main turbine system and the auxiliary high-pressure cylinder HP2 is not limited, the main turbine system may be arranged in a single shaft or in a split shaft, and the auxiliary high-pressure cylinder HP2 and the main turbine system may be arranged coaxially or in a split shaft.
For example, as shown in FIG. 2, the main turbine system employs a single shaft arrangement, and the auxiliary high pressure cylinder HP2 is arranged split from the main turbine system. Namely, high pressure cylinder HP1, intermediate pressure cylinder IP, first low pressure cylinder LP1 and second low pressure cylinder LP2 are coaxially arranged, and auxiliary high pressure cylinder HP2 and high pressure cylinder HP1 are coaxially arranged. A rotor output shaft of the high-pressure cylinder HP1 is provided with a first generator 61, and a rotor output shaft of the auxiliary high-pressure cylinder HP2 is provided with a second generator 62. Of course, the first generator 61 may be provided on the rotor output shaft of the second low pressure cylinder LP 2.
As shown in fig. 3, the main turbine system employs a single shaft arrangement, and the auxiliary high-pressure cylinder HP2 is connected with the rotor shaft of the high-pressure cylinder HP1 through an automatic synchronizing clutch 7. Namely, high pressure cylinder HP1, intermediate pressure cylinder IP, first low pressure cylinder LP1 and second low pressure cylinder LP2 are coaxially arranged, and auxiliary high pressure cylinder HP2 is coaxially arranged with high pressure cylinder HP 1. The rotor output shaft of the second low pressure cylinder LP2 is provided with the first generator 61.
As shown in fig. 4, the main turbine system adopts a split shaft arrangement, high pressure cylinder HP1 is split shaft arranged with intermediate pressure cylinder IP, first low pressure cylinder LP1 and second low pressure cylinder LP2 are coaxially arranged, and auxiliary high pressure cylinder HP2 is connected with the rotor shaft of high pressure cylinder HP1 through automatic synchronizing clutch 7, that is, auxiliary high pressure cylinder HP2 is coaxially arranged with high pressure cylinder HP 1. The rotor output shaft of the intermediate pressure cylinder IP is provided with a first generator 61, and the rotor output shaft of the high pressure cylinder HP1 is provided with a second generator 62. Of course, the first generator 61 may be provided on the rotor output shaft of the second low pressure cylinder LP 2.
When the arrangement shown in fig. 3 and 4 is adopted, synchronous grid connection and online disconnection of the auxiliary high-pressure cylinder HP2 can be realized through opening and closing of the auxiliary steam inlet valve group 21. Specifically, when the unit operates in the first operation mode, the second operation mode or the third operation mode, the auxiliary steam inlet valve group 21 is closed, the automatic synchronizing clutch 7 is automatically disengaged, and the auxiliary high-pressure cylinder HP2 is disconnected; when the load of the unit rises and an operation mode four or an operation mode five needs to be adopted, the auxiliary steam inlet valve group 21 is opened, the auxiliary high-pressure cylinder HP2 is started, and when the rotating speed of the auxiliary high-pressure cylinder HP2 rises to be equal to that of the high-pressure cylinder HP1 of the main turbine system, the automatic synchronous clutch 7 can realize automatic engagement and locking, so that synchronous grid-connected power generation of the auxiliary high-pressure cylinder HP2 is realized; when the load of the unit is obviously reduced and the unit needs to be switched to the first operation mode, the second operation mode or the third operation mode, the automatic synchronizing clutch 7 is unlocked, then the auxiliary steam inlet valve group 21 is closed, the steam inlet of the auxiliary high-pressure cylinder HP2 is blocked, the rotating speed of the auxiliary high-pressure cylinder HP2 is reduced, and the automatic synchronizing clutch 7 is automatically disengaged, so that the online disconnection of the auxiliary high-pressure cylinder HP2 is realized.
Of course, the arrangement form of the main turbine system and the auxiliary high-pressure cylinder HP2 of the present invention is not limited to the above three forms of the present embodiment, and other forms may be adopted.
In summary, in the single reheat steam turbine with parallel high-pressure cylinders according to the embodiment, by providing the auxiliary high-pressure cylinder HP2, in terms of thermodynamic design, the maximum capacity of the main turbine system high-pressure cylinder HP1 through-flow design can be reduced to less than 80% of that of the existing steam turbine, and the main steam pressure, the regenerative steam extraction pressure and the final water supply temperature under the partial load working condition can be effectively improved, so that the economy of the partial load working condition is improved. Meanwhile, the auxiliary high-pressure cylinder HP2 is combined with the heater bypass adjustment, so that the economy of the unit under the high-load working condition can be improved, and the economy of the rated-load working condition is guaranteed on the basis of increasing the capacity of the unit. Therefore, the single reheat steam turbine with the high-pressure cylinders connected in parallel can improve the economical efficiency of thermodynamic cycle, and especially can improve the overall economical efficiency of a unit under wide and low load working conditions.
The above description is only a preferred embodiment of the present invention, and it should be noted that, for those skilled in the art, various modifications and substitutions can be made without departing from the technical principle of the present invention, and these modifications and substitutions should also be regarded as the protection scope of the present invention.
Claims (7)
1. A single reheat steam turbine with parallel high pressure cylinders, comprising a main turbine system and an auxiliary high pressure cylinder (HP2), the main turbine system comprising a high pressure cylinder (HP1), an intermediate pressure cylinder (IP), low pressure cylinders (LP1, LP2) and a reheater (4), the inlet of the high pressure cylinder (HP1) being in communication with a high pressure steam pipe (100), and the outlet being in communication with the inlet of the reheater (4) through a cold reheat steam pipe (200); the steam inlet of the auxiliary high-pressure cylinder (HP2) is communicated with the high-pressure steam pipeline (100) through an auxiliary steam inlet pipeline (300), the steam outlet is communicated with the cold reheating steam pipeline (200) through an auxiliary steam outlet pipeline (400), and an auxiliary steam inlet valve group (21) is arranged on the auxiliary steam inlet pipeline (300); the outlet of the reheater (4) is communicated with the steam inlet of the intermediate pressure cylinder (IP) through a hot reheat steam pipeline (500); a high-pressure steam extraction port is arranged on the high-pressure cylinder (HP1), a first steam extraction pipeline (701) leading to the first heater (31) is connected to the high-pressure steam extraction port, the first heater (31) is connected with a first bypass (801) in parallel, and a first adjusting valve group (51) is arranged on the first bypass (801); a second steam extraction pipeline (702) leading to a second heater (32) is connected to a steam outlet of the high-pressure cylinder (HP1), the second heater (32) is connected with a second bypass (802) in parallel, and a second regulating valve group (52) is arranged on the second bypass (802);
with the gradual increase of the unit load, the single reheat steam turbines of the parallel high-pressure cylinders sequentially realize the following operation modes: in the first operation mode, the auxiliary steam inlet valve group (21) is closed, high-pressure steam in the high-pressure steam pipeline (100) completely enters a high-pressure cylinder (HP1) of the main turbine system, no high-pressure steam flows into the auxiliary high-pressure cylinder (HP2), the first regulating valve group (51) and the second regulating valve group (52) are both closed, and the first bypass (801) and the second bypass (802) are not used;
in the second operation mode, the auxiliary steam inlet valve group (21) is closed, high-pressure steam in the high-pressure steam pipeline (100) completely enters a high-pressure cylinder (HP1) of the main turbine system, no high-pressure steam flows into the auxiliary high-pressure cylinder (HP2), the first regulating valve group (51) is opened, the first bypass (801) is used, the second regulating valve group (52) is closed, and the second bypass (802) is not used;
in the third operation mode, the auxiliary steam inlet valve group (21) is closed, high-pressure steam in the high-pressure steam pipeline (100) completely enters a high-pressure cylinder (HP1) of the main turbine system, no high-pressure steam flows into the auxiliary high-pressure cylinder (HP2), the first regulating valve group (51) and the second regulating valve group (52) are both opened, and the first bypass (801) and the second bypass (802) are both put into use;
the fourth operation mode is that the auxiliary steam inlet valve group (21) is opened, one part of high-pressure steam in the high-pressure steam pipeline (100) enters a high-pressure cylinder (HP1) of the main turbine system, the other part of high-pressure steam enters an auxiliary high-pressure cylinder (HP2) through the auxiliary steam inlet valve group (21), the first adjusting valve group (51) and the second adjusting valve group (52) are both closed, and the first bypass (801) and the second bypass (802) are not used;
and in the fifth operation mode, the auxiliary steam inlet valve group (21) is opened, one part of high-pressure steam in the high-pressure steam pipeline (100) enters a high-pressure cylinder (HP1) of the main turbine system, the other part of high-pressure steam enters an auxiliary high-pressure cylinder (HP2) through the auxiliary steam inlet valve group (21), the first regulating valve group (51) is opened, the first bypass (801) is put into use, the second regulating valve group (52) is closed, and the second bypass (802) is not put into use.
2. The single reheat steam turbine with parallel high pressure cylinders of claim 1, wherein a high pressure steam inlet valve group (22) is provided at a steam inlet of the high pressure cylinder (HP 1).
3. The single reheat steam turbine with parallel high pressure cylinders according to claim 1, wherein the intermediate pressure cylinder (IP) is provided with a first intermediate pressure steam extraction port and a second intermediate pressure steam extraction port, the first intermediate pressure steam extraction port and the second intermediate pressure steam extraction port are respectively connected with a third steam extraction pipeline (703) leading to a third heater (33) and a fourth steam extraction pipeline (704) leading to a fourth heater (34), and the third heater (33) and the fourth heater (34) are respectively connected in parallel with a third bypass (803) and a fourth bypass (804).
4. The single reheat steam turbine with parallel high pressure cylinders according to claim 3, wherein a third regulating valve group (53) and a fourth regulating valve group (54) are respectively provided on the third bypass (803) and the fourth bypass (804).
5. The single reheat steam turbine of parallel high pressure cylinders, according to any of claims 1 to 4, wherein the main turbine system is in a single shaft arrangement, and the auxiliary high pressure cylinder (HP2) is in a split shaft arrangement with the main turbine system; and a rotor output shaft of the high-pressure cylinder (HP1) or the low-pressure cylinder (LP2) is provided with a first generator (61), and a rotor output shaft of the auxiliary high-pressure cylinder (HP2) is provided with a second generator (62).
6. The single reheat steam turbine of parallel high pressure cylinders, according to any of claims 1 to 4, wherein the main turbine system employs a single shaft arrangement, and the auxiliary high pressure cylinder (HP2) is connected with the rotor shaft of the high pressure cylinder (HP1) through an automatic synchronizing clutch (7); and a rotor output shaft of the low pressure cylinder (LP2) is provided with a first generator (61).
7. The single reheat steam turbine of parallel high pressure cylinders, according to any of claims 1 to 4, characterized in that the high pressure cylinder (HP1) is split-shaft arranged with the intermediate pressure cylinder (IP) which is coaxially arranged with the low pressure cylinders (LP1, LP2), the auxiliary high pressure cylinder (HP2) is connected with the rotor shaft of the high pressure cylinder (HP1) through an automatic synchronizing clutch (7); and a rotor output shaft of the intermediate pressure cylinder (IP) or the low pressure cylinder (LP2) is provided with a first generator (61), and a rotor output shaft of the high pressure cylinder (HP1) is provided with a second generator (62).
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| CN111042880B (en) * | 2018-10-12 | 2024-04-05 | 上海明华电力科技有限公司 | Wide-load efficient turbine unit with high-pressure cylinders coaxially distributed in separate cylinders |
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| CN114233416B (en) * | 2021-12-07 | 2022-09-23 | 暨南大学 | Dynamically-reconstructed steam turbine generator unit and operation method |
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| CN114810240B (en) * | 2022-04-14 | 2023-05-09 | 暨南大学 | A high-efficiency steam turbine unit with an external multi-channel regulating system and its operating method |
| CN114922704B (en) * | 2022-05-18 | 2024-03-26 | 西安热工研究院有限公司 | A steam turbine power generation system that can operate safely at low load |
| CN117211912A (en) * | 2022-06-02 | 2023-12-12 | 上海汽轮机厂有限公司 | Double-machine recuperation small steam turbine back pressure control thermal system and its control method |
| CN115263456B (en) * | 2022-07-26 | 2026-03-31 | 暨南大学 | A combined regulating dynamic reconfiguration steam turbine generator set and its operation method |
| CN120720089B (en) * | 2025-08-22 | 2026-01-13 | 东方电气集团东方汽轮机有限公司 | A steam turbine system with composite dynamic steam distribution and wide-range coordinated operation and its operation method |
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