CN110686227A - Intermediate reheat steam power generation system - Google Patents
Intermediate reheat steam power generation system Download PDFInfo
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- CN110686227A CN110686227A CN201911051358.6A CN201911051358A CN110686227A CN 110686227 A CN110686227 A CN 110686227A CN 201911051358 A CN201911051358 A CN 201911051358A CN 110686227 A CN110686227 A CN 110686227A
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F22—STEAM GENERATION
- F22B—METHODS OF STEAM GENERATION; STEAM BOILERS
- F22B31/00—Modifications of boiler construction, or of tube systems, dependent on installation of combustion apparatus; Arrangements of dispositions of combustion apparatus
- F22B31/08—Installation of heat-exchange apparatus or of means in boilers for heating air supplied for combustion
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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
- F01K13/00—General layout or general methods of operation of complete plants
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F22—STEAM GENERATION
- F22D—PREHEATING, OR ACCUMULATING PREHEATED, FEED-WATER FOR STEAM GENERATION; FEED-WATER SUPPLY FOR STEAM GENERATION; CONTROLLING WATER LEVEL FOR STEAM GENERATION; AUXILIARY DEVICES FOR PROMOTING WATER CIRCULATION WITHIN STEAM BOILERS
- F22D11/00—Feed-water supply not provided for in other main groups
- F22D11/02—Arrangements of feed-water pumps
- F22D11/06—Arrangements of feed-water pumps for returning condensate to boiler
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F22—STEAM GENERATION
- F22G—SUPERHEATING OF STEAM
- F22G5/00—Controlling superheat temperature
- F22G5/12—Controlling superheat temperature by attemperating the superheated steam, e.g. by injected water sprays
- F22G5/123—Water injection apparatus
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- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02P—CLIMATE CHANGE MITIGATION TECHNOLOGIES IN THE PRODUCTION OR PROCESSING OF GOODS
- Y02P80/00—Climate change mitigation technologies for sector-wide applications
- Y02P80/10—Efficient use of energy, e.g. using compressed air or pressurized fluid as energy carrier
- Y02P80/15—On-site combined power, heat or cool generation or distribution, e.g. combined heat and power [CHP] supply
Abstract
The invention provides an intermediate reheating steam power generation system, which comprises a boiler, a first steam turbine and a second steam turbine, wherein the boiler comprises a superheater, a first reheater and a second reheater; the first steam turbine comprises a first high-pressure cylinder and a first low-pressure cylinder, a steam inlet of the first high-pressure cylinder is communicated with an outlet of the superheater, a steam outlet of the first high-pressure cylinder is communicated with a steam inlet of the second reheater, a steam inlet of the first low-pressure cylinder is communicated with a steam outlet of the second reheater, and a steam outlet of the first low-pressure cylinder is communicated with an inlet of the superheater; the second steam turbine comprises a second high-pressure cylinder and a second low-pressure cylinder, a steam inlet of the second high-pressure cylinder is communicated with an outlet of the superheater, a steam outlet of the second high-pressure cylinder is communicated with a steam inlet of the first reheater, a steam inlet of the second low-pressure cylinder is communicated with a steam outlet of the first reheater, and a steam outlet of the second low-pressure cylinder is communicated with an inlet of the superheater. The invention can reasonably distribute the high-temperature reheated steam and reduce the occupied area of the general diagram of the system.
Description
Technical Field
The invention relates to the technical field of steam power generation, in particular to an intermediate reheat steam power generation system.
Background
Blast furnace gas is a high-quality secondary energy source as a byproduct of an iron-making process of iron and steel enterprises. The blast furnace gas power generation project belongs to the energy-saving technology of the iron and steel industry which is emphatically encouraged and promoted by the nation. At present, most iron and steel enterprises are equipped with gas generator sets with medium temperature and medium voltage parameters and above, along with the saturated state of the development of the power industry, steam turbine plants begin to develop towards high-parameter small-sized steam turbines, and gas power generation projects with ultrahigh pressure parameters and above are produced. In view of that the efficiency of the ultrahigh-pressure (pressure is more than 13.7 MPa) intermediate reheating generator set can be improved by more than 25% compared with the high-temperature and high-pressure (pressure is more than 8.83MPa and temperature is more than 540 ℃), the old generator set is replaced by the ultrahigh-pressure intermediate reheating generator set by each enterprise.
In some steel enterprises, more than two old generator sets are arranged, the original generators in the plant still run stably, the equipment state is good, the land occupation in the plant is very tight, and the total map occupation can not be enlarged. Therefore, the reconstruction project which is beneficial to the old original generator and factory building and only reconstructs the boiler and the steam turbine is generated. As shown in fig. 1 and 2 (the direction of the arrow in the figure is the flow direction of steam), the intermediate reheat steam turbine generator units are all unit heating systems with one boiler for one machine (i.e. one boiler 100 'corresponds to one steam turbine 200'). When the transformation project is met, if the unit system mode of one furnace to one machine is continuously maintained, the overall map occupies a large area, and the whole equipment arrangement is not opened.
Two generating set's thermodynamic system divides unit system (as shown in fig. 1) and main control system (as shown in fig. 2) two kinds, compare in main control system, its equipment that corresponds also need shut down when having an equipment trouble to shut down in the unit system, and main control system then moves more nimble, there is an equipment trouble can be amputated and do not influence other equipment operation, however, when two steam turbine 200's load is inconsistent, steam turbine 200 'is also different to two high temperature reheat steam pressure requirements, adopt main control system as reheat steam, must cause high temperature reheat steam to be unable to distribute, cause the unit can't move.
Disclosure of Invention
The invention aims to provide an intermediate reheat steam power generation system which can realize that one boiler is provided with two turbines, can effectively reduce the occupied area of a system general diagram, and can not cause the situation that high-temperature reheat steam cannot be distributed.
To achieve the above object, the present invention provides an intermediate reheat steam power generation system, comprising:
the boiler comprises a boiler body, wherein a superheater, a first reheater and a second reheater are sequentially arranged in the boiler body along the flow direction of flue gas;
the first steam turbine comprises a first high-pressure cylinder and a first low-pressure cylinder, wherein a steam inlet of the first high-pressure cylinder is connected with an outlet of the superheater in a switching mode, a steam outlet of the first high-pressure cylinder is connected with a steam inlet of the second reheater in a switching mode, a steam inlet of the first low-pressure cylinder is connected with a steam outlet of the second reheater in a switching mode, and a steam outlet of the first low-pressure cylinder is connected with an inlet of the superheater in a switching mode;
and the second steam turbine comprises a second high-pressure cylinder and a second low-pressure cylinder, a steam inlet of the second high-pressure cylinder is connected with an outlet of the superheater in a break-make manner, a steam outlet of the second high-pressure cylinder is connected with a steam inlet of the first reheater in a break-make manner, a steam inlet of the second low-pressure cylinder is connected with a steam outlet of the first reheater in a break-make manner, and a steam outlet of the second low-pressure cylinder is connected with an inlet of the superheater in a break-make manner.
The intermediate reheat steam power generation system as described above, wherein the outlet of the superheater is connected with a high pressure steam header pipe, the high pressure steam header pipe is communicated with the steam inlet of the first high pressure cylinder through a first branch pipe, the high pressure steam header pipe is communicated with the steam inlet of the second high pressure cylinder through a second branch pipe, and both the first branch pipe and the second branch pipe are provided with a cut-off device.
In the intermediate reheat steam power generation system described above, the shutoff device is an electric gate valve or a pneumatic gate valve.
In the intermediate reheat steam power generation system, the steam outlet of the first high-pressure cylinder is communicated with the steam inlet of the second reheater through a first low-temperature reheat steam pipeline, and a first steam outlet check valve is arranged on the first low-temperature reheat steam pipeline;
and the steam outlet of the second high-pressure cylinder is communicated with the steam inlet of the first reheater through a second low-temperature reheated steam pipeline, and a second steam outlet check valve is arranged on the second low-temperature reheated steam pipeline.
The intermediate reheat steam power generation system as described above, wherein a first high pressure bypass pipe is connected between the first branch pipe and the first low temperature reheat steam pipe, and an inner diameter of the first high pressure bypass pipe is smaller than an inner diameter of the first branch pipe;
and a second high-pressure bypass pipeline is connected between the second branch pipe and the second low-temperature reheating steam pipeline, and the inner diameter of the second high-pressure bypass pipeline is smaller than that of the second branch pipe.
The intermediate reheat steam power generation system as described above, wherein a first attemperation and pressure reduction valve and a first water spray attemperation valve are connected to the first high pressure bypass line;
and the second high-pressure bypass pipeline is connected with a second temperature and pressure reducing valve and a second water spraying temperature reducing valve.
In the intermediate reheat steam power generation system, the steam inlet of the first low pressure cylinder is communicated with the steam outlet of the second reheater through a first high temperature reheat steam pipeline, and a first water spray desuperheater is arranged on the first high temperature reheat steam pipeline;
and a steam inlet of the second low-pressure cylinder is communicated with a steam outlet of the first reheater through a second high-temperature reheated steam pipeline, and a second water spray desuperheater is arranged on the second high-temperature reheated steam pipeline.
The intermediate reheat steam power generation system as described above, wherein a first flue damper door is provided between the superheater and the first reheater, and a second flue damper door is provided between the first reheater and the second reheater.
The intermediate reheat steam power generation system comprises a first low-pressure steam generator, a second high-pressure steam generator, a first high-temperature reheat steam pipeline, a second high-temperature reheat steam pipeline, a first low-pressure bypass pipeline, a second low-pressure bypass pipeline, a first low-pressure bypass pipeline and a second high-temperature reheat steam pipeline, wherein the first low-pressure bypass pipeline is arranged between the first low-pressure steam generator and the second high-temperature reheat steam pipeline.
The intermediate reheat steam power generation system as described above, wherein a third attemperation and depressurization valve and a third water spray attemperation valve are provided on the first low pressure bypass pipe;
and a fourth temperature and pressure reducing valve and a fourth water spraying temperature and temperature reducing valve are arranged on the second low-pressure bypass pipeline.
Compared with the prior art, the invention has the following advantages:
according to the intermediate reheat steam power generation system, the two reheaters are arranged in the boiler, and are respectively and correspondingly communicated with the two turbines, so that one boiler can work with the two turbines, the occupied area and the investment cost of a system general diagram are effectively reduced, the problem that high-temperature reheat steam cannot be distributed when the loads of the turbines are different is effectively solved, the safe and stable operation of the system is realized, and in addition, only one auxiliary machine system of the boiler needs to be matched, so that the operation is simple and convenient;
according to the intermediate reheat steam power generation system, the first high-pressure bypass pipeline, the first low-pressure bypass pipeline, the second high-pressure bypass pipeline and the first low-pressure bypass pipeline are arranged, so that high-pressure steam can be subjected to temperature and pressure reduction and then connected to the first condenser and/or the second condenser without influencing the normal operation of a boiler when the first turbine and/or the second turbine carry out load shedding;
according to the intermediate reheat steam power generation system, the temperature of high-temperature reheat steam exhausted from the first reheater and the second reheater can be accurately controlled through the coordinated control of the smoke damper door and the water spray desuperheater, so that the operation of controlling the temperature of steam output by a boiler is more flexible.
Drawings
The drawings are only for purposes of illustrating and explaining the present invention and are not to be construed as limiting the scope of the present invention. Wherein:
FIG. 1 is a schematic diagram of a prior art system of units;
FIG. 2 is a block diagram of a prior art policing system;
FIG. 3 is a schematic diagram of the intermediate reheat steam power generation system of the present invention.
The reference numbers illustrate:
the prior art is as follows:
100', a boiler; 200' and a steam turbine;
the invention comprises the following steps:
1. a boiler; 11. a furnace body; 12. a superheater; 13. a first reheater; 14. a second reheater;
15. a first flue damper door; 16. a second flue gas damper door;
2. a first turbine; 21. a first high pressure cylinder; 22. a first low pressure cylinder;
3. a second turbine; 31. a second high pressure cylinder; 32. a second low pressure cylinder;
4. a high pressure steam main; 41. a first branch pipe; 42. a second branch pipe;
5. a first low temperature reheat steam line; 51. a first high pressure bypass conduit;
6. a second low temperature reheat steam line; 61. a second high pressure bypass conduit;
7. a first high temperature reheat steam line; 71. a first water spray desuperheater;
8. a second high temperature reheat steam line; 81. a second water spray desuperheater;
9. a water return main pipe;
91. a first return branch pipe; 911. a first low pressure bypass conduit;
92. a second return branch pipe; 921. a second low pressure bypass line.
Detailed Description
In order to clearly understand the technical solution, the purpose and the effect of the present invention, a detailed description of the present invention will be described with reference to the accompanying drawings. Wherein the use of "high pressure" and "low pressure", "high temperature" and "low temperature" are merely for ease of relative reference between sets of terms and do not describe any particular limitation on the modified terms. The terms "first", "second", etc. are used for descriptive purposes only and are not to be construed as indicating or implying a relative importance or implicitly indicating the number of technical features indicated, whereby a feature defined as "first", "second", etc. may explicitly or implicitly include one or more of such features.
As shown in fig. 3, the present invention provides an intermediate reheat steam power generation system comprising a boiler 1, a first turbine 2 and a second turbine 3, wherein:
the boiler 1 comprises a boiler body 11, specifically, the boiler 1 is a steam boiler 1 with improved primary intermediate reheating type, single drum, natural circulation, centralized downcomer and pi-shaped arrangement, the specific structure of the steam boiler 1 is the prior art, and is not described herein again, different from the prior art, a superheater 12, a first reheater 13 and a second reheater 14 are sequentially arranged in the boiler body 11 along the flow direction of flue gas, wherein the superheater 12 can heat the temperature of steam to above 480 ℃, and the boiler 1 framework adopts an all-steel welding structure;
the first steam turbine 2 comprises a first high pressure cylinder 21 and a first low pressure cylinder 22, the specific structure of the first steam turbine 2 is the prior art, and details are not repeated herein, a steam inlet of the first high pressure cylinder 21 can be connected with an outlet of the superheater 12 in an on-off manner, a steam outlet of the first high pressure cylinder 21 can be connected with a steam inlet of the second reheater 14 in an on-off manner, a steam inlet of the first low pressure cylinder 22 can be connected with a steam outlet of the second reheater 14 in an on-off manner, a steam outlet of the first low pressure cylinder 22 can be connected with an inlet of the superheater 12 in an on-off manner, specifically, high-temperature high-pressure steam discharged from the superheater 12 can enter the first high pressure cylinder 21, the first high pressure cylinder 21 utilizes the high-temperature high-pressure steam to work and then discharges low-temperature steam, the discharged low-temperature steam can enter the second reheater 14 and is heated by the second reheater 14 to form high-temperature reheated steam, the high-temperature reheated steam can enter the first low pressure, the first low-pressure cylinder 22 utilizes the high-temperature reheated steam to do work and then discharges low-temperature steam, the low-temperature steam is cooled to become condensate water, the condensate water flows back into the superheater 12 and is subjected to heating treatment by the superheater 12 to form high-temperature high-pressure steam again, the formed high-temperature high-pressure steam enters the first high-pressure cylinder 21, and the cycle operation is carried out;
the second steam turbine 3 includes a second high pressure cylinder 31 and a second low pressure cylinder 32, the specific structure of the first steam turbine 2 is the prior art, and details are not repeated herein, a steam inlet of the second high pressure cylinder 31 can be connected with an outlet of the superheater 12 in an on-off manner, a steam outlet of the second high pressure cylinder 31 can be connected with a steam inlet of the first reheater 13 in an on-off manner, a steam inlet of the second low pressure cylinder 32 can be connected with a steam outlet of the first reheater 13 in an on-off manner, a steam outlet of the second low pressure cylinder 32 can be connected with an inlet of the superheater 12 in an on-off manner, specifically, high-temperature and high-pressure steam discharged from the superheater 12 enters the second high pressure cylinder 31, the second high pressure cylinder 31 utilizes the high-temperature and high-pressure steam to work and then discharge low-temperature steam, the discharged low-temperature steam enters the first reheater 13 and is subjected to a heating treatment by the first reheater 13 to form high-temperature reheated steam, and the high-, the second low pressure cylinder 32 uses the high temperature reheated steam to do work and discharge low temperature steam, the low temperature steam is cooled to become condensate water, the condensate water flows back into the superheater 12, the condensate water is subjected to heating treatment through the superheater 12 to form high temperature and high pressure steam again, the formed high temperature and high pressure steam again enters the second high pressure cylinder 31, and the cycle operation is performed.
It should be noted that, the arrow direction in fig. 3 is the flow direction of the flue gas, the steam and the condensed water, the connection capable of being made and broken can be realized by arranging valves, and under the condition that the intermediate reheat steam power generation system normally operates, each valve is in a normally open state.
According to the intermediate reheat steam power generation system, two reheaters are arranged in the boiler 1, and the two reheaters are respectively and correspondingly communicated with the two turbines, so that one boiler 1 can work with the two turbines, the occupied area and the investment cost of a system general diagram are effectively reduced, the problem that high-temperature reheat steam cannot be distributed when the loads of the turbines are different is effectively solved, the safe and stable operation of the system is realized, and in addition, only one auxiliary machine system of the boiler 1 needs to be matched, so that the operation is simple and convenient.
In one embodiment of the present invention, as shown in fig. 3, the outlet of the superheater 12 is connected to a high pressure steam manifold 4, the high pressure steam manifold 4 is communicated with a steam inlet of the first high pressure cylinder 21 through a first branch pipe 41, the high pressure steam manifold 4 is communicated with a steam inlet of the second high pressure cylinder 31 through a second branch pipe 42, specifically, the high pressure steam manifold 4 is connected to the first branch pipe 41 and the second branch pipe 42 in parallel, the first branch pipe 41 is communicated with a steam inlet of the first high pressure cylinder 21, the second branch pipe 42 is communicated with a steam inlet of the second high pressure cylinder 31, the first branch pipe 41 and the second branch pipe 42 are arranged such that the first high pressure cylinder 21 and the second high pressure cylinder 31 can simultaneously introduce high temperature and high pressure steam in the high pressure steam manifold 4, both the first branch pipe 41 and the second branch pipe 42 are provided with a cut-off device (not shown), when the first steam turbine 2 and/or the second steam turbine 3 fails, the cutoff device can cut off the first branch pipe 41 and/or the second branch pipe 42 in time so that the high-temperature and high-pressure steam discharged from the superheater 12 cannot flow into the first high-pressure cylinder 21 and/or the second high-pressure cylinder 31 to facilitate the maintenance operation of the first steam turbine 2 and/or the second steam turbine 3.
Further, the cutting device is an electric gate valve or a pneumatic gate valve, so as to avoid the situation that the manual cut-off valve cannot cut off the first branch pipe 41 and/or the second branch pipe 42 due to the large pressure of the high-temperature and high-pressure steam, and thus the cutting device can cut off the first branch pipe 41 and/or the second branch pipe 42 timely and quickly.
Specifically, electric gate valve includes valve body and electric actuator, and electric actuator drives the valve rod through the motor and moves from this to open or close the valve during normal operating, and the concrete structure and the theory of operation that start the gate valve are prior art, and no longer give unnecessary details here.
Further, the steam outlet of the first high pressure cylinder 21 is communicated with the steam inlet of the second reheater 14 through a first low temperature reheat steam pipe 5, and the first low temperature reheat steam pipe 5 is provided with a first steam outlet check valve (not shown in the figure); the steam outlet of the second high-pressure cylinder 31 is communicated with the steam inlet of the first reheater 13 through the second low-temperature reheat steam pipeline 6, a second steam outlet check valve (not shown in the figure) is arranged on the second low-temperature reheat steam pipeline 6, and the first steam outlet check valve and the second steam outlet check valve can prevent steam from flowing backwards so as to ensure the safety of the intermediate reheat steam power generation system in the using process.
Further, a first high pressure bypass pipe 51 is connected between the first branch pipe 41 and the first low temperature reheat steam pipe 5, an inner diameter of the first high pressure bypass pipe 51 is smaller than an inner diameter of the first branch pipe 41, specifically, a relation between the inner diameter of the first high pressure bypass pipe 51 and the inner diameter of the first branch pipe 41 satisfies that a steam flow flux of the first high pressure bypass pipe 51 is not more than 60% of a steam flow flux of the first branch pipe 41, so that when the first turbine 2 is load shedding, steam pressure in the first branch pipe 41 can be shared by the first high pressure bypass pipe 51 without affecting operation of the boiler 1, a second high pressure bypass pipe 61 is connected between the second branch pipe 42 and the second low temperature reheat steam pipe 6, an inner diameter of the second high pressure bypass pipe 61 is smaller than an inner diameter of the second branch pipe 42, specifically, a relation between the inner diameter of the second high pressure bypass pipe 61 and the inner diameter of the second branch pipe 42 satisfies that a steam flow flux of the second high pressure bypass pipe 61 is not more than that the second branch Is 60% of the steam flow, so that when the second turbine 3 is load shedding, the steam pressure in the second branch pipe 42 can be shared through the second high pressure bypass pipe 61, thereby not affecting the operation of the boiler 1.
Still further, a first temperature and pressure reducing valve (not shown in the figure) and a first water spraying temperature and temperature reducing valve (not shown in the figure) are connected to the first high-pressure bypass pipeline 51, the first temperature and pressure reducing valve and the first water spraying temperature and temperature reducing valve are both electric control valves, the specific structures and working principles of the first temperature and pressure reducing valve and the first water spraying temperature and temperature reducing valve are both in the prior art, and are not described herein again, a second temperature and pressure reducing valve (not shown in the figure) and a second water spraying temperature and temperature reducing valve (not shown in the figure) are connected to the second high-pressure bypass pipeline 61, the second temperature and pressure reducing valve and the second water spraying temperature and temperature reducing valve are both electric control valves, the specific structures and working principles of the second temperature and pressure reducing valve and the second water spraying temperature and temperature reducing valve are both in the prior art, and are not described herein again, specifically, the first water spraying temperature and temperature reducing valve are both communicated with an external low-temperature water source, and the first high-pressure reducing And the flow rate of steam in the second high pressure bypass pipe 61, the temperature of steam entering the first and second high pressure bypass pipes 51 and 61 can be precisely controlled by controlling the opening degrees of the first and second water spray attemperation valves, so that the steam entering the second reheater 14 via the first high pressure bypass pipe 51 and the steam entering the first reheater 13 via the second high pressure bypass pipe 61 satisfy the use requirement, thereby enabling the boiler 1 to be normally operated.
In one embodiment of the present invention, as shown in fig. 3, the steam inlet of the first low pressure cylinder 22 is communicated with the steam outlet of the second reheater 14 through a first high temperature reheat steam pipe 7, and the first high temperature reheat steam pipe 7 is provided with a first water spray attemperator 71; the steam inlet of the second low-pressure cylinder 32 is communicated with the steam outlet of the first reheater 13 through the second high-temperature reheated steam pipeline 8, the second water spray desuperheater 81 is arranged on the second high-temperature reheated steam pipeline 8, and the first water spray desuperheater 71 and the second water spray desuperheater 81 are arranged to cool the high-temperature reheated steam so that the temperature of the high-temperature reheated steam can meet the use requirement.
Further, a first flue gas damper 15 is disposed between the superheater 12 and the first reheater 13, a second flue gas damper 16 is disposed between the first reheater 13 and the second reheater 14, and the opening degree of the first flue gas damper 15 and the second flue gas damper 16 is adjusted to adjust the amount of flue gas passing through the first reheater 13 and the second reheater 14 so as to control the heating temperature of the first reheater 13 and the second reheater 14, and the temperature of the high-temperature reheated steam discharged from the first reheater 13 and the second reheater 14 can be precisely controlled by using the first water spray attemperator 71 and the second water spray attemperator 81 in combination, specifically, for example, the temperature of the high-temperature reheated steam discharged from the first reheater 13 is controlled, if the temperature of the high-temperature reheated steam discharged from the first reheater 13 is too high, the opening degree of the first flue gas damper 15 can be reduced so as to reduce the flue gas passing through the first reheater 13, therefore, the heat exchange effect of the first reheater 13 is reduced, and at this time, if the temperature of the high-temperature reheated steam discharged from the first reheater 13 is still high, the operation of the second water spray desuperheater 81 is controlled to reduce the temperature of the high-temperature reheated steam, and the manner of controlling the temperature of the high-temperature reheated steam discharged from the second reheater 14 is the same as that of controlling the temperature of the high-temperature reheated steam discharged from the first reheater 13, and thus, the description thereof will not be repeated.
Further, a steam exhaust port of the first low pressure cylinder 22 is connected with a first condenser (not shown in the figure), a steam exhaust port of the second low pressure cylinder 32 is connected with a second condenser (not shown in the figure), an inlet of the superheater 12 is connected with a water return manifold 9, the water return manifold 9 is communicated with the first condenser through a first water return branch pipe 91, the water return manifold 9 is communicated with the second condenser through a second water return branch pipe 92, specifically, the water return manifold 9 is connected with a first water return branch pipe 91 and a second water return branch pipe 92 in parallel, the first water return branch pipe 91 is communicated with the steam exhaust port of the first low pressure cylinder 22 through the first condenser, the second water return branch pipe 92 is communicated with the steam exhaust port of the second low pressure cylinder 32 through the second condenser, a first low pressure bypass pipeline 911 is arranged between the first condenser and the first high temperature reheat steam pipeline 7, specifically, a relation between an inner diameter of the first low pressure bypass pipeline 911 and an inner diameter of the first water return branch pipe 91 satisfies that a steam flux of the first low pressure bypass pipeline 911 is not 60% of the steam circulation of a return water branch pipe 91, like this when first turbine 2 gets rid of the load, the accessible is first high pressure bypass pipeline 51 and first low pressure bypass pipeline 911 connect to first condenser after reducing the temperature and reducing the pressure with high-pressure steam and do not influence boiler 1 normal operating, be equipped with second low pressure bypass pipeline 921 between second condenser and the second high temperature reheat steam pipe 8, concretely, the relation between the internal diameter of second low pressure bypass pipeline 921 and the internal diameter of second return water branch pipe 92 satisfies that the steam circulation of second low pressure bypass pipeline 921 is not more than 60% of the steam circulation of second return water branch pipe 92, like this when second turbine 3 gets rid of the load, accessible second high pressure bypass pipeline 61 and second low pressure bypass pipeline 921 connect to the second condenser after reducing the temperature and reducing the pressure with high-pressure steam and do not influence boiler 1 normal operating.
Further, a third temperature and pressure reducing valve (not shown in the figure) and a third water spraying temperature and temperature reducing valve (not shown in the figure) are arranged on the first low-pressure bypass pipeline 911, both the third temperature and pressure reducing valve and the third water spraying temperature and temperature reducing valve are electric regulating valves, and the specific structures and working principles of the third temperature and pressure reducing valve and the third water spraying temperature and temperature reducing valve are the prior art, and are not described herein again; be equipped with fourth pressure and temperature reducing valve (not shown in the figure) and fourth water spray temperature reducing valve (not shown in the figure) on the second low pressure bypass pipeline 921, fourth pressure and temperature reducing valve and fourth water spray temperature reducing valve are electrical control valve, and the concrete structure and the theory of operation of fourth pressure and temperature reducing valve and fourth water spray temperature reducing valve are prior art, no longer describe herein, it is specific, third water spray temperature reducing valve and fourth water spray temperature reducing valve all are linked together with outside low temperature water source, can accurate control the steam flow that gets into in first low pressure bypass pipeline 911 and second low pressure bypass pipeline 921 through adjusting the aperture of third pressure and temperature reducing valve and fourth pressure and temperature reducing valve, can accurate control the temperature of the steam that gets into in first low pressure bypass pipeline 911 and second low pressure bypass pipeline 921 through controlling the aperture of third pressure and fourth water spray temperature reducing valve, so that the steam that gets into over heater 12 via first low pressure bypass pipeline 911 and via second low pressure bypass pipeline satisfies the use demand Thereby enabling the boiler 1 to be normally operated.
The operation of the intermediate reheat steam power generation system of the present invention will be described in detail with reference to the accompanying drawings:
as shown in fig. 3, the high-temperature and high-pressure steam discharged from the superheater 12 is introduced into the first high-pressure cylinder 21 and the second high-pressure cylinder 31 through a first branch pipe 41 and a second branch pipe 42 connected to the high-pressure steam header pipe 4;
the first high-pressure cylinder 21 utilizes high-temperature high-pressure steam to do work and then discharges low-temperature steam, the discharged low-temperature steam is introduced into the second reheater 14 through the first low-temperature reheated steam pipeline 5 and is subjected to heating treatment through the second reheater 14 to form high-temperature reheated steam, the high-temperature reheated steam enters the first low-pressure cylinder 22 through the first high-temperature reheated steam pipeline 7, the first low-pressure cylinder 22 utilizes the high-temperature reheated steam to do work and then discharges the low-temperature steam, the low-temperature steam enters the first condenser to be condensed into condensate water, the condensate water flows back into the superheater 12 through the first water return branch pipe 91 and the water return header pipe 9 and is subjected to heating treatment through the superheater 12 to form high-temperature high-pressure steam again, the formed high-temperature high-pressure steam again enters the first high-pressure cylinder 21 through the first branch pipe 41 connected to the;
during the above cycle, if the temperature of the high-temperature and high-pressure steam exhausted from the second reheater 14 is too high, the opening degree of the second damper door 16 is controlled to decrease to reduce the flue gas passing through the second reheater 14, so as to reduce the heat exchange amount of the second reheater 14, and at this time, if the temperature of the high-temperature reheated steam exhausted from the second reheater 14 is still higher, the first water spray attemperator 71 is controlled to operate to reduce the temperature of the high-temperature reheated steam; when the first turbine 2 is in load shedding, the high-pressure steam is subjected to temperature reduction and pressure reduction through the first high-pressure bypass pipeline 51 and the first low-pressure bypass pipeline 911 and then is connected to the first condenser, so that the normal operation of the boiler 1 can be prevented from being influenced;
the second high-pressure cylinder 31 utilizes the high-temperature high-pressure steam to do work and then discharges low-temperature steam, the discharged low-temperature steam is led into the first reheater 13 through the second low-temperature reheated steam pipeline 6 and is heated by the first reheater 13 to form high-temperature reheated steam, the high-temperature reheated steam enters the second low-pressure cylinder 32 through the second high-temperature reheated steam pipeline 8, the second low-pressure cylinder 32 utilizes the high-temperature reheated steam to do work and then discharges the low-temperature steam, the low-temperature steam enters the second condenser to be condensed into condensed water, the condensed water flows back into the superheater 12 through the second water return branch pipe 92 and the water return main pipe 9 and is heated by the superheater 12 to form high-temperature high-pressure steam again, the formed high-temperature high-pressure steam enters the second high-pressure cylinder 31 through the second branch pipe 42 connected to the high-pressure steam;
similarly, during the above cycle, if the temperature of the high-temperature and high-pressure steam discharged from the first reheater 13 is too high, the opening degree of the first flue gas damper 15 is controlled to decrease so as to reduce the flue gas passing through the first reheater 13, thereby reducing the heat exchange amount of the first reheater 13, and at this time, if the temperature of the high-temperature reheated steam discharged from the first reheater 13 is still high, the second water spray desuperheater 81 is controlled to operate so as to reduce the temperature of the high-temperature reheated steam; when the second turbine 3 is load shedding, the high-pressure steam is cooled and depressurized through the second high-pressure bypass pipeline 61 and the second low-pressure bypass pipeline 921 and then is connected to the second condenser, so that the normal operation of the boiler 1 can be prevented from being influenced.
In summary, in the intermediate reheat steam power generation system, two reheaters are arranged in the boiler, and the two reheaters are respectively and correspondingly communicated with the two turbines, so that one boiler can work with the two turbines, the occupation area and the investment cost of a system general diagram are effectively reduced, the problem that high-temperature reheat steam cannot be distributed when the loads of the turbines are different is effectively solved, the safe and stable operation of the system is realized, and in addition, only one auxiliary system of the boiler needs to be configured, so that the operation is simple and convenient;
according to the intermediate reheat steam power generation system, the first high-pressure bypass pipeline, the first low-pressure bypass pipeline, the second high-pressure bypass pipeline and the first low-pressure bypass pipeline are arranged, so that high-pressure steam can be subjected to temperature and pressure reduction and then connected to the first condenser or the second condenser without influencing the normal operation of a boiler when the first turbine or the second turbine is subjected to load shedding;
according to the intermediate reheat steam power generation system, the temperature of high-temperature reheat steam exhausted from the first reheater and the second reheater can be accurately controlled through the coordinated control of the smoke damper door and the water spray desuperheater, so that the operation of controlling the temperature of steam output by a boiler is more flexible.
The above description is only an exemplary embodiment of the present invention, and is not intended to limit the scope of the present invention. Any equivalent changes and modifications that can be made by one skilled in the art without departing from the spirit and principles of the invention should fall within the protection scope of the invention. It should be noted that the components of the present invention are not limited to the above-mentioned whole application, and various technical features described in the present specification can be selected to be used alone or in combination according to actual needs, so that the present invention naturally covers other combinations and specific applications related to the invention.
Claims (10)
1. An intermediate reheat steam power generation system, said intermediate reheat steam power generation system comprising:
the boiler comprises a boiler body, wherein a superheater, a first reheater and a second reheater are sequentially arranged in the boiler body along the flow direction of flue gas;
the first steam turbine comprises a first high-pressure cylinder and a first low-pressure cylinder, wherein a steam inlet of the first high-pressure cylinder is connected with an outlet of the superheater in a switching mode, a steam outlet of the first high-pressure cylinder is connected with a steam inlet of the second reheater in a switching mode, a steam inlet of the first low-pressure cylinder is connected with a steam outlet of the second reheater in a switching mode, and a steam outlet of the first low-pressure cylinder is connected with an inlet of the superheater in a switching mode;
and the second steam turbine comprises a second high-pressure cylinder and a second low-pressure cylinder, a steam inlet of the second high-pressure cylinder is connected with an outlet of the superheater in a break-make manner, a steam outlet of the second high-pressure cylinder is connected with a steam inlet of the first reheater in a break-make manner, a steam inlet of the second low-pressure cylinder is connected with a steam outlet of the first reheater in a break-make manner, and a steam outlet of the second low-pressure cylinder is connected with an inlet of the superheater in a break-make manner.
2. The intermediate reheat steam power generation system of claim 1,
the high-pressure steam main pipe is communicated with a steam inlet of the first high-pressure cylinder through a first branch pipe, the high-pressure steam main pipe is communicated with a steam inlet of the second high-pressure cylinder through a second branch pipe, and the first branch pipe and the second branch pipe are provided with cutting devices.
3. The intermediate reheat steam power generation system of claim 2,
the cutting device is an electric gate valve or a pneumatic gate valve.
4. The intermediate reheat steam power generation system of claim 2,
the steam outlet of the first high-pressure cylinder is communicated with the steam inlet of the second reheater through a first low-temperature reheating steam pipeline, and a first steam outlet check valve is arranged on the first low-temperature reheating steam pipeline;
and the steam outlet of the second high-pressure cylinder is communicated with the steam inlet of the first reheater through a second low-temperature reheated steam pipeline, and a second steam outlet check valve is arranged on the second low-temperature reheated steam pipeline.
5. The intermediate reheat steam power generation system of claim 4,
a first high-pressure bypass pipeline is connected between the first branch pipe and the first low-temperature reheat steam pipeline, and the inner diameter of the first high-pressure bypass pipeline is smaller than that of the first branch pipe;
and a second high-pressure bypass pipeline is connected between the second branch pipe and the second low-temperature reheating steam pipeline, and the inner diameter of the second high-pressure bypass pipeline is smaller than that of the second branch pipe.
6. The intermediate reheat steam power generation system of claim 5,
the first high-pressure bypass pipeline is connected with a first temperature and pressure reducing valve and a first water spraying temperature and temperature reducing valve;
and the second high-pressure bypass pipeline is connected with a second temperature and pressure reducing valve and a second water spraying temperature reducing valve.
7. The intermediate reheat steam power generation system of any one of claims 1 to 6,
the steam inlet of the first low-pressure cylinder is communicated with the steam outlet of the second reheater through a first high-temperature reheating steam pipeline, and a first water spray desuperheater is arranged on the first high-temperature reheating steam pipeline;
and a steam inlet of the second low-pressure cylinder is communicated with a steam outlet of the first reheater through a second high-temperature reheated steam pipeline, and a second water spray desuperheater is arranged on the second high-temperature reheated steam pipeline.
8. The intermediate reheat steam power generation system of claim 7,
and a first flue gas baffle door is arranged between the superheater and the first reheater, and a second flue gas baffle door is arranged between the first reheater and the second reheater.
9. The intermediate reheat steam power generation system of claim 7,
the steam exhaust port of the first low-pressure cylinder is connected with a first condenser, the steam exhaust port of the second low-pressure cylinder is connected with a second condenser, the inlet of the superheater is connected with a return water main pipe, the return water main pipe is communicated with the first condenser through a first return water branch pipe, the return water main pipe is communicated with the second condenser through a second return water branch pipe, the first condenser is provided with a first low-pressure bypass pipeline between first high-temperature reheat steam pipelines, and the second condenser is provided with a second low-pressure bypass pipeline between second high-temperature reheat steam pipelines.
10. The intermediate reheat steam power generation system of claim 9,
a third temperature and pressure reducing valve and a third water spraying temperature and temperature reducing valve are arranged on the first low-pressure bypass pipeline;
and a fourth temperature and pressure reducing valve and a fourth water spraying temperature and temperature reducing valve are arranged on the second low-pressure bypass pipeline.
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Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN111425274A (en) * | 2020-04-16 | 2020-07-17 | 京能(赤峰)能源发展有限公司 | Combined heat and power generation system capable of meeting resident and industrial heat supply requirements during deep peak shaving |
| CN112682827A (en) * | 2021-01-11 | 2021-04-20 | 北京京诚科林环保科技有限公司 | Coal gas power generation double-desuperheating water heating system and method |
| CN113432112A (en) * | 2021-06-29 | 2021-09-24 | 华电莱州发电有限公司 | Method for controlling rear main steam temperature of high-temperature superheater of boiler |
| CN114810250A (en) * | 2022-04-14 | 2022-07-29 | 重庆赛迪热工环保工程技术有限公司 | Power generation thermodynamic system for reducing heat loss of steam turbine exhaust |
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2019
- 2019-10-31 CN CN201911051358.6A patent/CN110686227A/en active Pending
Cited By (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN111425274A (en) * | 2020-04-16 | 2020-07-17 | 京能(赤峰)能源发展有限公司 | Combined heat and power generation system capable of meeting resident and industrial heat supply requirements during deep peak shaving |
| CN112682827A (en) * | 2021-01-11 | 2021-04-20 | 北京京诚科林环保科技有限公司 | Coal gas power generation double-desuperheating water heating system and method |
| CN113432112A (en) * | 2021-06-29 | 2021-09-24 | 华电莱州发电有限公司 | Method for controlling rear main steam temperature of high-temperature superheater of boiler |
| CN113432112B (en) * | 2021-06-29 | 2022-06-07 | 华电莱州发电有限公司 | Method for controlling rear main steam temperature of boiler high-temperature superheater |
| CN114810250A (en) * | 2022-04-14 | 2022-07-29 | 重庆赛迪热工环保工程技术有限公司 | Power generation thermodynamic system for reducing heat loss of steam turbine exhaust |
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